Hydraulic or pneumatic machine with tilting blades

ABSTRACT

This invention refers to a hydraulic or pneumatic machine with tilting blades, running either as an engine on a fluid flow or on pressure fluid or as a pump or a compressor. The hydraulic or pneumatic machine on a fluid flow according to the invention consists of a cylindrical casing with inlet and outlet openings, radially arranged, diametrically oposed, along the fluid flowing direction, some disk like rotors with tilting blades, hinged over their front faces and provided with driving mechanisms of their own, and some fixed drums located between the rotors, concentrically to them, making inside the machine some channels, symetrically arranged on one or several stages. Flowing through the channels, the fluid drives the tilting blades causing the movement of the rotors, all the rotors moving to one sense being coupled to the same outlet shaft of the machine. The tilting blades of the hydraulic or pneumatic machine operating according to the invention with pressure fluid, run in variable depth grooves located in the rings between the front faces of the rotors and connected to the fluid circuit, the operation conditions of the machine—motor or pump—being determined by the moving sense of the blade in the groove.

TECHNICAL FIELD OF THEE INVENTION

The invention pertains to a hydraulic or pneumatic machine with tiltingblades in simple and solid construction which can be built in variousconstructional variants, meant to run with high efficiency as an enginefed by a fluid stream, pressure stream or pressure gases resulted fromfuel combustion or as a pump or compressor with a broad range ofindustrial applications.

BACKGROUND OF THE INVENTION

There is a large variety of hydraulic or pneumatic machines having therotor equipped with swinging or tilting blades round a fixed shaft onthe rotor parallel or perpendicularly to its rotation axis driven by itsown weight, by the centrifugal force or by its own driving mechanisms.During a full rotor rotation, the blades are putting up the maximumresistance to the motion to the fluid stream sense taking over part ofits energy and the minimum resistance to the motion to the oppositesense of the fluid stream.

Such machines have the disadvantage of a sturdy, sophisticated, lowefficiency construction.

There are also hydraulic or pneumatic machines—motors or pumps—usingpressure working fluids, being equipped either with gliding blades inthe rotor or hinged blades on it, having the disadvantage of very narrowapplication ranges from the point of view of the working parameters andof a very elaborate execution in terms of accuracy, a rapid wearing ofthe active elements, very high stresses in the rotors bearings and anoutlet couple with variable value.

The technical issue solved by this invention consists in the executionof a hydraulic or pneumatic machine having rotors provided with tiltingblades which assures the taking over of the moving energy of the wholeamount of fluid throughout and can be integrated—alone or in a batteryof machines—in units to capture the energy of a moving fluid for a verywide range of fluid flow rates.

DISCLOSURE OF INVENTION

The hydraulic or pneumatic machine with tilting blades according to theinvention permits to achieve the goal as it can be built in variousconstructional variants, running either as a hydraulic or pneumaticmotor on fluid stream with one stage, made up of a cylindrical casingwith flat or shaped lids and radial inlet and outlet nozzles for theworking fluid, diametrically opposed, arranged to the fluid flowdirection, two coaxial disc like rotors, having the diameters close tothat of the casing, found under rotation movement in the opposite senseto one another due to some shaped tilting blades—of a rectangular shape,or, eventually, having two opposite curve sides—radially arranged or inan angle to the radius, hinged onto the neighbouring front surfaces ofthe two rotors, towards their periphery, the angle formed in the hinge,between the rotor surface and that of the associated blade, having thevertex arranged to the moving sense of each rotor and the values varyingduring the rotor rotation—between 0°—when the blade is in passiveposition, eventually located in a properly shaped seat on the face ofthe respective rotor—and a maximum angle of 90° eventually—when theblade is in active position, the position of the tilting blades on eachrotor being driven, during the rotor rotation, by a driving mechanism ofits own, with cams, known in themselves; a cylindrical dram locatedbetween the front faces provided with the tilting blades of the rotors,coaxial with them, fixed onto the machine casing by a shaped deflectorand a rib found within the symmetry plane of the inlet—outlet nozzle, sothat inside the machine are formed two channels of the channel, theinstantaneous motive force arising in each compartment of the respectivezone being proportional to the depth difference of the channel, in thatmoment, near the two tilting blades delimiting each compartment and thepressure of the respective compartment; a pump or a compressor, if anglevertex between the blade and the face of the rotor is orientated to theopposite sense of the rotor moving sense, the shaft of which is drivenby an outside couple, the fluid being sucked in this case in the finalzone of the channel and compressed in its initial zone; in variousconstructive variants either on the faces of a cylindrical ring may beprovided with several channels, independent or coupled between them, inseries—through some intermediate, shaped channels—or in parallel, makingdifferent circuits accordingly, coupled or independent ones having thesame functional role or various roles, the driving mechanisms of thetilting blades being orientated according to the position of the channelor of the respective circuit or in case the machine is staged, the fluidcircuits from various stages being coupled by means of some connectingpipes or by some spacer rings with the corresponding inner channelslocated between the cylindrical rings of each stage, in a variant, inorder to diminish the axial forces resulting in the bearings of therotors shafts the machine having at all the stages only rotors withtilting blades on both faces whereas in another variant it has a singleoutlet shaft locating one or several similar rotors, with tilting bladeson one or both front faces, the machine being able to run as a pneumaticmotor—fed on pressure gas coming from an outside tank or from the fuelcombustion in a combustion room equipped with feeding devices, for theformation of the fuel mixture and its ignition, known inthemselves-ensuring expansion of the working gas in one channel or aprolonged expansion in several coupled channels, or as a hydraulic motorfed on a pressure liquid, or as a pump or compressor, or with bothmotive and independent pumping circuits. Against the known solutions,the hydraulic or pneumatic machine, according to the invention, hasseveral advantages, such as:

the possibility to make highly efficient motors on fluid flow, havingreduced size rotors and low value starting couple due to the fluidcirculation through the machine in symmetrically arranged channels onone or several stages and to the flow concentrations due to theconvergent shape of the respective channel whereas the energy conversionsystem is coupled to the motor shaft—an electric generatoreventually—located outside the fluid flow;

the possibility to build sturdy machines with a low number of partsunder rotation and a very low number or no number of parts at all undertranslator motion, with low values of forces and relative velocities inthe contact points between the parts;

the possibility to build motors with quasiconstant couple at the outletshafts;

the possibility to build balanced machines with axial and radial forceshaving minimum values in the rotors bearings;

the possibility of making pneumatic machines, engines or compressorswhere the prolonged expansion or fluid compression respectively isachieved in circuits consisting of one or several channels coupled inseries or in parallel, the small pressure differences between thecompartments formed along the channels, between the successive blades ofeach rotor, resulting in low stresses in the tilting blades and in thebearings thereof as well as in low pressure loss values between thesuccessive compartments or towards the outside;

the possibility of achieving a large constructional variety of units tomake best use of the kinetic energy of a fluid flow, with constant orvariable direction continuous or intermittent flow, floating or fixedunits, in unsophisticated, solid construction and with small overalldimensions;

the possibility of making a wide constructional variety of hydraulic orpneumatic machines for static pressure fluids, with one or severalcircuits having the same functional role—motor or pump—or differentroles, with the same fluid in all circuits or with different fluids;

the possibility to make a thermal machine with a low number of parts orno parts at all under translator movement, with high mechanicalefficiency, having the combustion room incorporated inside or outside,with the compression circuits of the air or the fuel mixture and burnedgases expansion circuits respectively located in the same or differentmachines.

Herein under are several examples of the way the invention ismaterialised making also reference to FIGS. 1+123.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1—Cross section in vertical plane of a hydraulic or pneumaticmachine, according to the invention, in one constructional variant;

FIG. 2—Cross section in horizontal plane, to line I-I of FIG. 1;

FIG. 3—Cross section of the upper rotor, in a constructional variant;

FIG. 4—Partial top view of the upper rotor B shown in FIG. 3;

FIG. 5—Cross section of the lower rotor C in a constructional variant;

FIG. 6—Partial top view of the lower rotor C shown in FIG. 5;

FIG. 7, 8—Top view of tilting blade 12, in various constructionalvariants;

FIG. 9+11—Cross section to line II-II shown in FIG. 8, 9 of the tiltingblade 12 in various constructional variants;

FIG. 12—Cross section to line III-III shown in FIG. 6, of a shapedchannel b;

FIG. 13+16—Partial view of a front face of a rotor (B, C) in variousconstructional variants;

FIG. 17—Cross section to line IV-IV of FIG. 16;

FIG. 18—Partial cross section in vertical plane of a hydraulic orpneumatic machine according to the invention, in a constructionalvariant;

FIG. 19—Partial view of a front face of a rotor (B, C) in anotherconstructional variant;

FIG. 20—Cross section to line V-V shown in FIG. 19;

FIG. 21—Partial view from the direction VI of the tilting blades drivingmechanisms shown in FIG. 1;

FIG. 22—Partial section to line VII-VII shown in FIG. 21;

FIG. 23—Partial section to line VIII-VIII shown in FIG. 21;

FIG. 24—Partial cross section in vertical plane of a machine accordingto the invention, with a constructional variant of the tilting bladedriving mechanism;

FIG. 25, 26—Partial view from direction IX with the schematic diagram ofthe moving sense of the blade and tappet in various assembling variants;

FIG. 27—Partial cross section in vertical plane of a machine accordingto the invention, in another constructional variant of the tilting bladedriving mechanism;

FIG. 28, 29—Partial cross section to line X-X with the schematicillustration of the moving sense of the tilting blade and the tappet invarious assembling variants;

FIG. 30—Detail of the guide faces of the cam no. 34;

FIG. 31—Detail of the guide faces of the cam no. 35;

FIG. 32+35—The schematic diagram of the lever driving mechanism shown inFIG. 21, in various constructional variant;

FIG. 36—Partial section, rotated in horizontal plane, to line XI-XIshown in FIGS. 33, 35 and 41;

FIG. 37—Assembling detail of the tappet at the driving mechanism shownin FIGS. 25, 26, in a constructional variant;

FIG. 38—Assembling detail of the tappet for the driving mechanism shownin FIGS. 28, 29, in a constructional variant;

FIG. 39, 40—Partial cross section in vertical plane of a machineaccording to the invention, in other constructional variants of thetilting blade driving mechanism;

FIG. 41, 42—Partial view from direction XII of the driving mechanism ofthe blades shown in FIG. 40 in various constructional variants;

FIG. 43—Partial cross section in vertical plane of a machine accordingto the invention, in another constructional variant of the tilting bladedriving mechanism;

FIG. 44, 45—Section to line XIII-XIII shown in FIG. 43, in variousconstructional variants;

FIG. 46—Section to line XIV-XIV shown in FIG. 43;

FIG. 47—Developed schematic diagram of the partial evolution of theblade on each rotor during its full rotation;

FIG. 48—Front view of deflector 46 in a constructional variant;

FIG. 49—Partial cross section in horizontal plane to line I-I shown inFIG. 1 in a constructional variant;

FIG. 50—Partial cross section in vertical plane to line XV-XV shown inFIG. 49;

FIG. 51—Schematic diagram of the coupling of opposite outlet shafts ofthe machine to a single outside shaft;

FIG. 52—Schematic diagram of a machine according to the invention withcoaxial outlet shafts coupled to a single outside shaft;

FIG. 53—Partial schematic diagram of an additional bearing located onthe lower lid, a variant to FIG. 52;

FIG. 54—Schematic diagram of a machine according to the invention withcoaxial outlet shafts coupled to a single outside shaft, in aconstructional variant;

FIG. 55—Partial, schematic diagram of an additional bearing located onthe upper lid, a variant to FIG. 54;

FIG. 56—Schematic diagram of a machine according to the invention in oneassembling variant;

FIG. 57, 58—Partial cross section in vertical plane of a hydraulic orpneumatic machine according to the invention with channels on twostages, in various constructional variants;

FIG. 59—Partial cross section, in vertical plane, of a hydraulic orpneumatic machine according to the invention with channels on threestages;

FIG. 60—Cross section to line XVI-XVI shown in FIG. 59;

FIG. 61—Cross section to line XVII-XVII shown in FIG. 60;

FIG. 62, 63—View from direction XVIII shown in FIG. 60 in variousconstructional variants,

FIG. 64—Partial cross section of a E type rotor;

FIG. 65+68—Partial cross section of a F type rotor in variousconstructional variants;

FIG. 69—Section to line XIX-XIX shown in FIGS. 65 and 73;

FIG. 70—Section to line XX-XX shown in FIGS. 66 and 74;

FIG. 71—Section to line XXI-XXI shown in FIGS. 67 and 75;

FIG. 72—Section to line XXII-XXII shown in FIGS. 68 and 76;

FIG. 73+76—Partial cross section of a G type rotor in variousconstructional variants;

FIG. 77—Detail of “hinge” type tilting blade;

FIG. 78—Detail of “hinge” type tilting blade matching that shown in FIG.77;

FIG. 79+81—Detail of the driving mechanism of the “hinge” type coaxialtilting blades in various constructional variants;

FIG. 82, 83—Detail of the synchronisation mechanism of the tiltingblades driving at various stages, arranged on the rotor outside, invarious constructional variants;

FIG. 84, 85—Detail of the synchronisation mechanism of the tiltingblades driving at various stages, arranged inside the rotors, in variousconstructional variants;

FIG. 86+88—Schematic cross section on 90°-270° centerline of amultistage machine with an even number of stages, in variousconstructional variants;

FIG. 89+91—Schematic cross section on 90°-270° centerline of amultistage machine with an uneven number of stages, in variousconstructional variants;

FIG. 92—Schematic front view of a cylindrical ring 92 according to aconstructional variant, with an open a channel;

FIG. 93—Cross section to line XXIII-XXIII shown in FIG. 92;

FIG. 94—Developed schematic diagram of the channel a profile in thecylindrical ring 92 according to the constructional variant with openchannel;

FIG. 95—Developed schematic diagram of the channel a profile in thecylindrical ring 92 according to the constructional variant with closedchannel;

FIG. 96—Developed schematic diagram of the channel a profile in thecylindrical ring 92 according to the constructional variant withoverlapped channels;

FIG. 97—Detail of fluid inlet according to a constructional variant;

FIG. 98—Cross section to line XXIV-XXIV shown in FIG. 97;

FIG. 99—Detail of fluid inlet according to other constructional variant;

FIG. 100—Cross section to line XXV-XXV shown in FIG. 99;

FIG. 101—Detail of fluid inlet according to other constructionalvariant;

FIG. 102—Cross section to line XXVI-XXVI shown in FIG. 101;

FIG. 103—Schematic diagram of the tilting blade 12 position in the zonehaving decreasing depth b of channel a according to two functionalvariants;

FIG. 104—Detail of fluid outlet according to a constructional variant;

FIG. 105—Cross section to line XXVII-XXVII shown in FIG. 104;

FIG. 106—Detail of fluid outlet according to other constructionalvariant;

FIG. 107—Cross section to line XXVIII-XXVIII shown in FIG. 106;

FIG. 108—Schematic diagram of fluid inlet, with incorporated combustionchamber, according to a constructional variant;

FIG. 109—Schematic diagram of fluid inlet connection to the outsidecombustion chamber, according to a constructional variant;

FIG. 110—Schematic front view of a cylindrical ring 92 with twoindependent channels a″₁, a″₂ on the same front face;

FIG. 111—Schematic diagram of a cylindrical ring 92 with two channelsa″₁, a″₂ coupled, in parallel on each face;

FIG. 112—Schematic diagram of a cylindrical ring 92 with two channelsa″₁, a″₂ coupled in series according to two functional variants—motor orcompressor (pump);

FIG. 113—Schematic diagram of a cylindrical ring 92 with the combustionchamber incorporated between two channels a″₁, a″₂ connected in series;

FIG. 114—Schematic section in vertical plane, of a hydraulic orpneumatic machine having channels with variable depth, according to aconstructional variant;

FIG. 115+117—Schematic section in vertical plane of a hydraulic orpneumatic machine, having channels with variable depth, with two stages,with axially balanced rotor, in various constructional variants;

FIG. 118+120—Schematic section in vertical plane of a hydraulic orpneumatic machine, having channels with variable depth, with a singleshaft, in various constructional variants;

FIG. 121,122—Schematic section in vertical plane of a hydraulic orpneumatic machine, having channels with variable depth, with two stages,with axially balanced rotors, one outlet shaft, according to variousconstructional variants;

FIG. 123—Schematic section in vertical plane of a hydraulic or pneumaticmachine, having channels with variable depth, balanced axial rotors,with the combustion chamber incorporated in the cylindrical ring 92,according to a constructional variant.

BEST MODE FOR CARRYING OUT EXAMPLE 1

The hydraulic or pneumatic machine with vertical shaft made according tothe invention consists of a fixed stator A, two disk like rotors, anupper one B and a lower one C, spaced from one another by a drum Dconnected onto stator A, all elements being in line, the parallel frontfaces of the two rotors being equipped with tilting blades which, due tosome driving mechanisms of their own, can take against the rotor eithera passive position—the blade in the front plane of the rotor, or anactive position—the blade inclined by an α≦90° angle against the frontface of said rotor. Inside the machine, two symmetrical, semicircularchannels a are formed and due to the manner the driving mechanisms arearranged within the machine, the blades of one rotor are in activeposition, obstructing the passage of respective channel while the bladesof the other rotor are in passive position, so that the circulatingfluid along the two channels a flowing to the same sense, actuates theblades found simultaneously in active position on the two rotors B and Cand dictates their movement to opposite direction from one another, eachrotor conveying the energy taken from circulating fluid to its shaft.

The stator A is made up of a cylindrical shell 1 locating on a radialdirection, diametrically opposed a fluid inlet 2 and an outlet 3, adetachable upper lid 4 and a lower lid 5 in interdependence with theshell 1. The inlet 2 and outlet 3 are eventually in the form ofconvergent or divergent nozzle respectively. The height of the passagesection of inlet 2 and outlet 3 nozzles at shell entrance, shall notexceed the distance between the front faces of the rotors B and C.

The upper B and lower C rotors are each made up of a flat ring plane 6with identical, equally spaced, shaped grooves b, on the front surfacedelimiting channel a, secured to a frame 7 forming one part to a disc 8and 9 respectively, provided with a hub 10, 11.

Some tilting blades 12 are hinged on each flat plane 6, in the shapedgrooves b.

Each tilting blade 12 consists either of a rectangular or a distortedrectangular panel c with two opposite sides d and e, curves-arches ofellipse, as the blade in active position is perpendicular onto the frontsurface of the rotor or makes together with it an α<90° angle, havingfastened on one of its straight sides a cylindrical hub f provided witha central orifice g.

The profile of the curve sides d and e is selected in such a manner as,when the blade is in active position, inclined by an angle α against thefront face of rotor, all the points of the respective side be on thesame cylindrical face.

The panel c has an upper flat face h, tangential to the hub face f and alower flat face i, representing the active face of the blade on which,when in operation, the fluid exerts its pressure.

In other constructional variants, in view of making the blade a solid ofequal strength and of improving the hydraulic efficiency of the machine,the lower face of panel c can be shaped to a curve i known in itself, orcan be also provided with stiffening ribs k.

The groove b has a semicylindrical face l connected to the front face ofthe ring plane 6 by means of a flat plane m and a surface n shaped tothe blade 12 shape. Each groove is delimited in the case of arectangular blade, at the outward end, by a flat surface o provided withan orifice p and at the other end, a flat surface q with an orifice r.In the case of the blade with curve sides, d and e, the groove isdelimited at the both ends by some is curve surfaces s and trespectively, with adequate profile.

The two orifices, p and r, are in line and serve to fix some radial oraxial—radial bearings 13 and 14, known in themselves. Blade fasteninginto the bearings 13 and 14 of the rotor is achieved by a shaft 15 fixedin the orifice g of the blade hub by known means, not shown in thedrawing, a shaft also used for blade actuation.

Each blade is directed together with its hub to the moving direction ofthe rotor it is mounted on, while the rotation axis of the blade,passing through the bearings 13 and 14 is either on the radial directionor it makes with the tangent to the inner circular outline of the plane6, run to the piercing point of respective axis a β<90° angle, with thevertex facing the rotor moving direction.

In a constructional variant, in the absence of plane 6, the rotorconsists of an external stiffening ring 16 provided with orifices p,fixed on the frame 7 which in provided with orifices r, by means of rods17, known in themselves, radial oriented, also meant as positionlimiters for the blades 12 found in passive position being shaped to theblade profile to this effect.

In case of large size rotors, in order to take over the axial loads dueto their own weight, on the ring 16 of the rotor, between the bearings13 of the blades 12, some equally spaced bolts 18 are fastened for thefree rotation on them of same rollers 19 with spherical surface. Therollers of upper rotor B installed toward the outer side of ring 16 areguided between a flat ring surface u of a cylindrical gap v provided atthe upper side of the shell 1 and the lid surface 4, while the guiderollers of the lower rotor C, installed toward the inner side of thering 16 are supported on the lower lid 5 of the stator A.

In another constructional variant blade 12 is bracketed, resting onlyagainst bearing 14 on the ring 7 and having the outer end free. Positionlimiters 20 are provided on ring 7 for the passive position of eachblade 12.

Each tilting blade 12 is provided with a driving mechanism, which can bebuilt in several constructional variants, of elements known inthemselves, the driving element of the blade being fastened on the endfacing the inner side of the shaft 15.

According to a first variant, the driving element is a lever 21, thefree end of which being provided with a fixed axle 22 on which a roller23 moves freely. All the rollers 23 of the upper rotor B are guidedbetween the upper guiding front surface w and the lower one x—of a fixedcircular guide cam 24, whereas those of the lower rotor C between thefront upper y and lower z guide surfaces of a fixed, circular cam 25.The two cams 24 and 25 have the same profile and are symmetricallyarranged against the symmetry plane passing through the axis ofinlet—outlet openings.

In another constructional variant, the driving element is a pinion 26geared on a tappet with rack 27 provided at the end with a fixed shaft22 with roller 23, guided by cams 24 or 25 respectively, the tappetbeing able to make a translation movement in a vertical guide a′ or,according to another variant b′, with a protection casing 28 ofmechanism, fixed on the rotor, the position of the vertical guideagainst the pinion 26 determines both its rotation sense and thereforethat of blade 12 during the translation movement of tappet, and theprofile of cams 24 and 25.

According to another constructional variant, the driving element is acone pinion 29 geared with a cone gear with vertical axis 30 ininterdependence and in line with a cylindrical gear 31 provided with aspindle 32 which can freely rotate in the bearing c′ of a protectioncasing 33 of the mechanism, fastened onto the rotor. The gear 31 engageswith the rack tappet 27 provided with a fixed shaft 22 having the roller23, the tappet being capable to execute a translation movement in ahorizontal guide d′ or, according to another variant e′, of casing 33,the guide position to gear 31 determines its sense of rotation andtherefore of the blade 12 during the tappet translation movement. Allthe rollers 23 of the upper rotor B are guided between some outer f′ andinner g′ radial, guiding surfaces of a fixed radial cam 34, while thoseof the lower rotor C, between the outer h′ and inner i′ guiding surfacesof a fixed radial cam 35. The two cams 34 and 35 have similar profilesand are symmetrically arranged against the symmetry plane runningthrough the axis of inlet and outlet openings.

According to these variants, the two guide surfaces of each cam 24, 25,34, 35 secure the closure of the cinematic chain of the blade drivingmechanism.

According to other constructional variants, the cams have one guidesurface each, closing of the cinematic couple of the blade drivingmechanism being achieved either by the direct action of fluid pressureover the active surface of the blade, adequately shaped, or byadditional elements, known in themselves, assuring the permanent contactof the roller with the cam surface.

Thus the roller 23 of the lever drive mechanism of the blade on theupper rotor B and lower rotor C respectively, is maintained undercontact to the surface w of came 24 and surface z of cam 25respectively, either due to a counterweight 36 installed on an extensioni′ of lever 21 in the case of upper rotor B or on lever arm 21, in thecase of lower rotor C, or due to a spring 37, known in itself, installedin line with the tilting blade axis and twisted to the right sense so asto press the roller 23 on the cam surface, having one end fixed in anorifice k′ provided in frame 7 and the other end resting in an orificej′ of lever 21. Under this variant, the blade tilting in active positionduring a full rotor rotation is secured by the profile of the contactsurfaces w and z respectively, while resetting and keeping of the bladein passive position on rotor are secured by the said elements 36 or 37.The aperture angle of the blade in active position is limited by meansof a stopper 38, known in itself, fastened onto the inner face of therotor frame 7, having the role to limit the rotation of lever 21 arm j′.

In another variant, the roller 23 of the lever drive mechanism of theblade on upper B and lower C rotors respectively, is kept into contactwith the cam 24 surface x and y of cam 25, either by installing acounterweight 36 on lever arm 21 for the upper rotor B, respectively onthe extension j′ of lever 21 for lower rotor C, or by a spring 37twisted to the right sense. According to this variant, blade tilting inactive position is assured by element 36 or 37 while resetting andkeeping of the blade in passive position are assured by the profile ofthe contact surface x and y, respectively.

In other constructional variants, when blades 12 are driven by verticalor horizontal tappets, the permanent contact between the rollers 23 andthe guide surfaces x and y of the cams 24 and 25 and g′ and i′ of thecams 34 and 35 respectively is maintained by means of compressed springs39 installed in guides a′ or b′ and d′ or e′ respectively, under tappetsends.

The cams 24, 25 and 34; 35 respectively are fixed inside the drum Dwhich is in line with the two rotors B and C, by means of ribs 40, knownin themselves.

In another constructional variant, the cams 24, having the guide surfacew and 25 having the guide surface z are located on the upper lid 4 andlower lid 5 respectively.

In this case casings 28 are installed with the guides a′ or b′ orientedto the rotors disks 8 and 9 respectively, provided with orifices m′,corresponding to the associated guides for passing the tappets 27, theircompression on the guide surfaces of cams being achieved by the springs39 installed under compression in the tappets guides.

In case of tappets drive, the aperture angle of the blade is limited bythe limitation of tappet stroke, chasing the suitable distance betweenits end and the guide bottom.

In another constructional variant, the tilting blades 12 of upper rotorB are guided by a front cam 41 with a guide surface n′, while those ofthe lower rotor C by a front cam 42 with a guide surface o′, both ofthem fixed in the fluid flowing channel a on the outer face of drum D,at its ends. The panel c of each blade is provided with a gap p′ each,corresponding to the modified profile of the fluid flowing a channel,due to the existence of the two cams. On the surface h of the panel ofeach tilting blade, in the contact zone with the cam's guide surface, askid 43 is fixed by known means with an r′ end the shape of which suitsthe contact with the cam surface, eventually provided with a contactroller, known in itself, not shown in the drawing, located in gap p′.

The driving mechanism of each blade consists of lever 21 without roller23, fixed on shaft 15, driven either by counterweight 36 or by spring37, as previously described, in order to assure blade lifting in activeposition, its resetting and keeping in passive position being assured bycams profile 41 and 42.

In another constructional variant, the tilting blade 12 can eitherrotate freely on shaft 15 fixed on the rotor, in orifices p and r, or itis fixed on shaft 15 installed in bearings 13 and 14, the drivingmechanism of the blade consisting of a twisting spring 44, known initself, located in an orifice s′ in line with orifice g, located at theend of the blade's hub f, one of the spring end being fixed in a gap t′existing in the wall of orifice s′, while the other is fixed in theorifice k′ of the rotor frame 7, so as the spring should be stressed inorder to assure, during the rotor movement, the permanent contactbetween the r′ end of skid 43 and the guide surface of the associatedcam and consequently blade 12 lifting from passive position to activeposition on rotor, when the cam profile allows it.

In these variants, angle α is limited either by the position of cams 41,42 against the front surface of respective rotor, for α<90°, or by thesurface m of groove b for α=90°.

During a complete rotor rotation, each blade makes a rotation movement,being at the same time capable to take, due to its own drivingmechanism, an active position, when the upper face h of blade isinclined by an angle α≦90° against the rotor front face, or a passiveposition when the upper face h of blade is on the rotor front surfaceplane, being eventually located in the shaped groove b, or a transitionphase from one position to other.

The angles described by a blade in one of the specific positions duringa complete rotation of the rotor are marked by γ:

γ₁—the angle described during the transition phase of the blade frompassive to active position;

γ₂—the angle described by the blade in active position;

γ₃—the angle described by the blade in the transition phase from activeto passive position;

γ₄—the angle described by the blade in passive position; on conditionthat γ₁+γ₂+γ₃+γ₄=360°.

The size of angle α as well as the length of time for maintaining theblade 12 in one of the said positions, during a full rotor rotation,expressed by the value of angles γ are determined by the cam profile ofthe blade driving mechanism. The profile identity of the two cams 24, 25and 34, 35 or 41, 42 respectively determines equal values for the pairsof angles γ specific to the two rotors, B and C.

Cams are fixed so as their guide surfaces should assure the symmetricalplane arrangement of angles γ₁+γ₄ specific to a rotor, against thosespecific to the other rotor, the symmetry plane running through the axisof stator A inlet—outlet openings.

The drum D consisting of a central body 45 with a cylindrical outer facehaving a deflector 46 and a rib 47, dyametrically opposed, provided withstrengthening plates 48 and 49, is connected to the stator A of themachine by means of spacers 50 and some fastening elements like bolts,nuts, known in themselves, not shown on the drawing, so that deflector46 and rib 47 be in the mentioned symmetry plane.

The deflector 46 has symmetrical lateral faces u′ making a sharp anglebetween them, connected to the outer face of body 45 along its fullheight.

Blade 12 tilting, in active position, due to its own driving mechanism,can start only after the blade, in passive position on the rotor underrotation movement, outdistanced, with its entire outline, the projectionof lateral surface u′ of deflector 46 on the front surface of theassociated rotor, while the return to passive position ends before theblade reaches near the rib 47. According to one constructional variant,deflector 46 is provided with gaps v′, having a curved face, known initself, permitting either the earlier start of blade tilting in activeposition, or deflector extension onto the angular zone γ₁.

Two symmetrical, semicircular channels are thus formed inside themachine, each channel having a rectangular passing section, defined bythe front surfaces of the two rotors B and C, under a rotation movementin opposite direction to one another, the stationary inner face ofstator A and the outer face of drum D.

In order to decrease hydraulic losses, the distance between the frontsurfaces of the two rotors as well as the diameters of shell 1 surfacesand of drum D body 45, are chosen function of blade 12 dimensions so asto secure minimum clearance from construction viewpoint between thewalls of the machine semicircular channel and the edges of the blades,in active position, in the respective channel.

According to a constructional variant, when the blade does not reach therotor outer edge, in order to reduce the clearance between the outeredge of the blade in active position on rotor and the cylindrical faceof the casing A, a cylindrical segment 51 is fixed on stator, in eachchannel, between the front faces of the two rotors B and C, within thezone covered by angle γ₂.

The two channels a directly connected to the inlet and outlet openings,allow separation of machine incoming fluid into two equal streamsflowing to the same direction.

By their profile and arrangement, the cams pairs assure blades 12tilting, in active working position and the return to passive positionof each rotor B and C, in one of the two channels a, so that, in eachchannel the blades of one rotor should be in active position,obstructing its section, while the blades of the other rotor should bein passive position.

The fluid working pressure in each channel exerted on the inner facecovered by angle α, of tilting blades 12 of one rotor, when the bladesare in active position in respective channel, determines the rotormovement to the fluid flow direction and the occurrence of an enginecouple at its shaft. Due to the fluid flowing to the same direction andto the symmetrical arrangement of the blades in active position on thetwo rotors, in the two machine channels, rotors B and C will move toopposite directions from one another, generating equal driving torque.

The number of tilting blades 12 on each rotor is selected in such amanner that between the fluid inlet and outlet openings should, at anytime, be at least one blade in active position to obturate channel a, soas not to allow direct fluid circulation between the two machineopenings.

Each rotor B and C by its 10 and 11 hub respectively, is fastened onto ashaft 52 and 53 respectively, through known means—wedges, grooves,etc.—not shown on drawings. The two in line shafts are supported againstcasing A by bearings 54 provided with sealing devices, all elementsbeing known, in orifice w′ on the upper lid 4 and orifice x′ on thelower lid 5. The shaft ends rotating to opposite direction from oneanother get out of the machine on each side of it and can be coupled toa power consumer each, by means of known couplings, not shown ondrawing.

According to a constructional variant, the machine has one outer shaft55 parallel to the in line shafts 52 and 53 of rotors B and C, supportedagainst an external bearing 56 connected on casing A by means of asupport 57, all elements being known in themselves.

On rotor B shaft 52 and rotor C shaft 53 is installed one cone gear 58and 59 respectively, in a mirror like arrangement, each one beingengaged with a cone gear 60 connected onto the end of an intermediateshaft 61 supported in a bearing 62 on the upper lid 4 and the lower lid5 of casing A, by means of a support 63.

The shafts 61, rotating to the same direction, drive by means of conepinions 64 on the other end of the shafts some cone gears 65 an shaft55, all elements being known in themselves.

In another constructional variant, the two in line shafts of the machineget out on one side, through one of the machine lids. To this effect, incase it gets out through the upper lid 4, the lower rotor C is mountedby its hub 11 onto a central shaft 66 whereas the upper rotor B ismounted by its hub 10 onto a tubular shaft 67 having a central channely′. The tubular shaft 67 gets out through the central orifice of theupper lid 4, resting on it by means of a radial—axial bearing 68 alsoprovided with a sealing device, all elements being known in themselves.The central shaft 66 rests on a radial—axial bearing 69, also providedwith a sealing device, mounted in the central channel y′ of a tubularshaft 67, according to one variant, it can additionally rest on abearing 70 provided on the lower lid 5. In case the shafts get outthrough the lower lid 5, the upper rotor B is mounted on the centralshaft 66 while the lower rotor C on the tubular shaft 67, its bearing 68being mounted in orifice x′ of the machine lower lid 5, the additionalbearing 70 being eventually provided on lid 4.

On the external ends of shafts 66 and 67 are fixed the cone gear wheels59 and 58 respectively, which rotate to opposite directions from oneanother and simultaneously engaged with a con pinion 71 on a machinedriving shaft 72, determine its movement to one direction, the motorpower at outlet shaft summing up the developed powers of the two rotors.The outlet shaft rests onto the lower lid 5, by means of a bearing 73provided with a support 74, all elements being known in themselves.

In another constructional variant, the two in line shafts 66 and 67represent the inlet shafts of a planetary reducer 75, known in itself,whose outlet shaft is coupled to a power consumer.

EXAMPLE 2

The hydraulic or pneumatic machine with vertical shaft, with multistagechannels, made according to the invention, allows the circulation of alarger fluid flow, as compared to the one in the preceding example, byincreasing the fluid passage section due to the use of several rotors ofsame diameter, namely: two extreme rotors with one front face each,provided with tilting blades 12, of which one, either the upper rotor Bor the lower rotor C is mounted on one of the machine shafts and theother, a ring rotor E without supporting elements on machine shaft, anda number of disk F or ring G intermediate rotors with two front faceseach, provided with tilting blades 12 on both faces, the blades on oneface being mirror like arranged to those on the other face, their sizeand number being the same for the front faces of the rotors on eachstage while they can vary from one stage to the other.

The tilting blades 12 of each rotor are arranged in such a manner as theneighbouring rotors move to opposite direction from one another, thedistance between the rotors front faces representing the height of thefluid flowing channel a at each machine stage.

All rotors moving to one sense are rigidly coupled between them, makingone package of rotors with the tilting blades 12 axes arranged on thesame vertical planes so as inside the machine be two packages of rotors,moving to opposite senses from one another, each package being coupledto one of the two machine shafts, to which they convey the motionreceived from the working fluid.

The upper B and lower C rotors are similarly from constructional pointof view to those given in the preceding example whereas the ring rotor Eis different from constructional point of view only through the absenceof the coupling elements on machine shaft-disk 8 or 9 respectively andthe hub 10 or 11 respectively—and can be mounted, both in upper andlower position, depending on the constructional variant chosen.

The intermediate disk like rotor F consists of a flat ring plane 6fixed, by means of disk 8, 9 respectively, onto hub 10, 11 respectivelythrough which it conveys the motion to one of the two machine shafts:upper and lower ones, respectively.

The ring plane 6 has two parallel front faces provided with shapedgrooves b made according to one of the variants described in theaforesaid example, each groove being provided with in line orifices pand r for the hinged fastening of blade 12 onto the rotor. The shapedgrooves b on the front face of plane 6 are symmetrically—mirrorlike—arranged as compared to those on the other front face, all beingarranged in such a manner as to secure the rotor, by the position of thetilting blade on respective surface, a rotation movement to the oppositesense of the two neighbouring rotors.

According to a constructional variant, the intermediate rotor F is madeof a ring 16, concentrically attached to frame 7, interdependent todisks 8, 9 and hubs 10, 11 respectively, through the rods 17, eventuallyarranged radial and which can also serve as position limiters for blades12 in passive position, shaped to this end according to blades profile.Both the ring 16 and the frame 7 are provided with coaxial orifices pand r respectively in order to mount the tilting blades pairs.

In another constructional variant, in order to reduce rotor F thickness,the rotor has the blades 12, located in opposite positions on the twofront faces, installed either on a single shaft or on coaxial shafts,the rotor being in this case provided with one row of orifices p and r.The two tilting blades 12, each have the hub made of one or severalelements f fixed on panel c edge and arranged along its entire length,alternatively with the ones making the hub of the pair blade thus makingtogether a “hinge” type articulation, either loose on the shaft 15 if itis connected in the corresponding orifices p and r of the rotor, orconnected by their hubs f, by known means, not shown on drawing, onedirectly on shaft 15 while the other—loose against shaft 15—fixed on atubular shaft 78, in line with it, in this latter case, thecorresponding p and r orifices of the rotor having installed thebearings 13 and 14 respectively, while the two shafts 15 and 78 aremeant for mounting the blades driving mechanism. Under this variant, inthe case of a rotor made up of a ring panel 6, the seat shaped for theincreasing the fluid passage section due to the use of several rotors ofsame diameter, namely: two extreme rotors with one front face each,provided with tilting blades 12, of which one, either the upper rotor Bor the lower rotor C is mounted on one of the machine shafts and theother, a ring rotor E without supporting elements on machine shaft and anumber of disk F or ring G intermediate rotors with two front faceseach, provided with tilting blades 12 on both faces, the blades on oneface being mirror like arranged to those on the other face, their sizeand number being the same for the front faces of the rotors on eachstage while they can vary from one stage to the other.

The tilting blades 12 of each rotor are arranged in such a manner as theneighbouring rotors move to opposite direction from one another, thedistance between the rotors front faces representing the height of thefluid flowing channel a at each machine stage.

All rotors moving to one sense are rigidly coupled between them, makingone package of rotors with the tilting blades 12 axes arranged on thesame vertical planes so as inside the machine be two packages of rotors,moving to opposite senses from one another, each package being coupledto one of the two machine shafts, to which they convey the motionreceived from the working fluid.

The upper B and lower C rotors are similarly from constructional pointof view to those given in the preceding example whereas the ring rotor Eis different from constructional point of view only through the absenceof the coupling elements on machine shaft-disk 8 or 9 respectively andthe hub 10 or 11 respectively—and can be mounted, both in upper andlower position, depending on the constructional variant chosen.

The intermediate disk like rotor F consists of a flat ring plane 6fixed, by means of disk 8, 9 respectively, onto hub 10, 11 respectivelythrough which it conveys the motion to one of the two machine shafts:upper and lower ones, respectively.

The ring plane 6 has two parallel front faces provided with shapedgrooves b made according to one of the variants described in theaforesaid example, each groove being provided with in line orifices pand r for the hinged fastening of blade 12 onto the rotor. The shapedgrooves b on the front face of plane 6 are symmetrically—mirrorlike—arranged as compared to those on the other front face, all beingarranged in such a manner as to secure the rotor, by the position of thetiling blade on respective surface, a rotation movement to the oppositesense of the two neighbouring rotors.

According to a constructional variant, the intermediate rotor F is madeof a ring 16, concentrically attached to frame 7, interdependent todisks 8, 9 and hubs 10, 11 respectively, through the rods 17, eventuallyarranged radial and which can also serve as position limiters for blades12 in passive position, shaped to this end according to blades profile.Both the ring 16 and the frame 7 are provided with coaxial orifices pand r respectively in order to mount the tilting blades pairs.

In another constructional variant, in order to reduce rotor F thickness,the rotor has the blades 12, located in opposite positions on the twofront faces, installed either on a single shaft or on coaxial shafts,the rotor being in this case provided with one row of orifices p and r.The two tilting blades 12, each have the hub made of one or severalelements f fixed on panel c edge and arranged along its entire length,alternatively with the ones making the hub of the pair blade thus makingtogether a “hinge” type articulation, either loose on the shaft 15 if itis connected in the corresponding orifices p and r of the rotor, orconnected by their hubs f, by known means, not shown on drawing, onedirectly on shaft 15 while the other—loose against shaft 15—fixed on atubular shaft 78, in line with it, in this latter case, thecorresponding p and r orifices of the rotor having installed thebearings 13 and 14 respectively, while the two shafts 15 and 78 aremeant for mounting the blades driving mechanism. Under this variant, inthe case of a rotor made up of a ring panel 6, the seat shaped for theinstallation of the in-line tilting blades pairs with coaxial hubs,results from crossing the opposite shaped grooves b on the respectivefront faces of the panel and is symmetrical to a plane containing therotation axes of the rotor blades, made up of the plane surfaces m, theshaped surfaces n as well as the ending surfaces of the two grooves.

The intermediate rotor G, in the form of a ring similar fromconstructional point of view to the above described intermediate rotorF, is devoid of the coupling elements to one of the machine shafts—disks8, 9 respectively and hubs 10, 11 respectively—being provided on bothfront faces with tilting blades 12 arranged in such a manner as tosecure a rotation movement to the opposite sense of its neighbouringrotors.

The machine can be built in several constructional variants, having aneven or uneven number of stages.

In a constructional variant, in the general case of a machine with aneven number of stages and uneven number of rotors consequently, the twopackages of rotors consist of:

one package H made up of extreme rotors, the upper rotor B and the ringrotor E loose against the machine shaft, with tilting blades on oneface, among which it can be found, in the case of the machines with anumber of stages >2, one or several intermediate rotors G₁, G₂ withtilting blades on both faces, all the rotors of the package beingrigidly fixed to one another by means of longitudinal tie-bars 76,equally spaced, along parallel or concurrent directions, on the outeroutline of the reeve rotors and provided with stiffening plates 77 andfastening elements—bolts and nuts—known in themselves, not shown on thedrawing. The whole package of rotors is coupled, by means of hub 10belonging to the rotor B, to one of the machine shafts, either to theoutlet one, at the upper side of machine 52 or 67, or to the centralshaft 66, when it gets out at the machine lower side.

In a constructional variant, the rotors package H is provided at itsupper side, with a ring rotor E, loose against the machine shaft,whereas at its lower side it is provided with an extreme rotor C, bywhose hub 11 the whole package of rotors is coupled to a shaft, eitherto the outlet one at the machine lower side 53 or 67, or to the centralshaft 66, when it gets out at the machine upper side; in the particularcase of a two staged machine, the rotors package H consists only of thetwo extreme rotors, without any intermediate rotor G:

a package I, consisting of one or several intermediate rotors F₁, F₃ . .. with tilting blades on both faces, each rotor being placed between twoneighbouring rotors, belonging to the other package of rotors H anddirectly coupled, by its hub, to the other shaft, according to theconstructional variant chosen for the rotors package H.

In a constructional variant, the rotors package I consists of oneintermediate rotor in the form of a disk F₁, located in the machine inthe vicinity of the extreme rotor B or C of the rotors package H, end anumber of intermediate rotors in the form of a ring G, all the rotors ofthe package being rigidly fixed to one another by means of longitudinaltie-bars 76 and of fastening plates 77, equally spaced on the inneroutline of the frame 7 of each rotor, inside the drums D the wholepackage of rotors being coupled to the machine shaft by the hub of therotor in the form of a disk F₁, the form of the ring rotors G permittingthe reduction of the gap inside the machine drums by shaping accordinglythe lid 4 or 5 placed in the vicinity of the extreme rotor E of therotors package H.

In another constructional variant, in the general case of a machine withan uneven number of stages >1—therefore, with an even number ofrotors—the two packages of rotors are made up of the following:

a J package consisting of the upper rotor B, with tilting blades on oneface and several intermediate rotors as rings G₁, G₂, having tiltingblades on both faces, fastened to one another by means of tie-bars 76and of fastening plates 77, the whole package being coupled by hub 10onto the upper rotor B, to one of the machine shafts, either the outletone at the upper side of the machine, 52 or 67, or to the central shaft66, when it gets out of the machine at its lower side.

In another constructional variant, the rotors package J is made up of anumber of intermediate rotors G₁, G₂ . . . and the lower rotor C, withtilting blades on one face, by whose hub 11, the whole package iscoupled to one machine shaft: either to the outlet one, at the lowerside of machine 53 or 67 or to the central shaft 66 when it gets out atthe upper side of machine.

a package K consisting of the other extreme rotor with tilting blades onone face, the upper rotor B and the lower rotor C respectively, and oneor several intermediate rotors F₁, F₂ . . . . with tilting blades onboth faces, intercalated between the rotors of the other package anddirectly coupled by its hub, each, to the other shaft of the machine,according to the variant chosen for the rotors package J.

In a constructional variant, the rotors package K consists of anintermediate rotor, as a disk F₁ located in the vicinity of the extremerotor B or C of the rotors package J, several intermediate rotors in theform of a ring G and an extreme annular rotor E, all the package rotorsbeing rigidly fixed among them by means of longitudinal tie-bars 76 andof fastening plates 77, equally spaced on the inner outline of the frame7 of each is rotor, inside the drum D, the whole rotors package beingcoupled to the machine shaft by the hub of the rotor in the form of adisk F₁ whereas the lid 4 or 5 placed in the vicinity of rotor E of thepackage is duly shaped so as to reduce the gap created inside the drumsD.

In the particular case of a one staged machine, the two rotors packagesJ and K are made up of one rotor each, either B or C, the constructionaltype being similar to that described under example 1.

Each machine stage, within the space farmed between the front faces oftwo neighbouring rotors, is provided with one drum D₁, D₂ . . . similarto that described in the previous example, equipped on its body 45 withthe deflector 46 and the rib 47, diametrically opposed, whose extremeedge do not exceed the outline of said rotors.

All the drums D₁, D₂ . . . are arranged in the same position, withdeflector 46 located in the symmetry plane of inlet nozzle and coupledto one another, making a package to be fixed onto one of the casing Alid of the machine. Fastening of the adjacent drums D₁, D₂ . . . to oneanother or of the whole package of drums to the casing lid is achievedeither through the rotor outside, in case they are located on both sidesof rotor directly coupled onto one of the machine shafts, or throughrotor inside, in case they are located on both sides of a rotor coupledto the others at the outside, by tie-bars 76.

Thus, the drums D located on both sides of an F type rotor, directlycoupled by its hub onto the machine shaft, are located to one another byrotor outside, using the fastening plates 48 and 49 respectively, ininterdependence with deflector 46 and the rib 47 respectively, betweenwhich spacers 79 are mounted by means of fastening parts which are notshown on the drawing, all elements being known in themselves. Likewise,the whole package of drums is fixed on one of casing A lids by theoutside of a rotor, directly coupled to the machine shaft by means ofshorter spacers 50, located between the fastening plates 48 and 49 ofthe drum and the associated lid.

The shape and size of the fastening plates 48 and 49 as well as thelocation of spacers 79, 50 respectively, are selected in such a manneras to permit both the movement of the rotors directly coupled to themachine shaft and the movement of the rotors belonging to the otherpackage, coupled at the outside, by means of tie-bars 76 while theclearance between the fixed parts and the moving ones should be minimumso as to diminish the hydraulic losses.

The drums D located on both sides of a rotor G coupled to the otherrotors of the package it belongs to, at the outside, by means oftie-bars 76, are fixed among them by means of fastening rings 80 locatedinside the body 45 of the drum, in interdependence with it and by meansof spacers 79 located between said rings, all elements being known inthemselves. Likewise, the whole package of drums is fixed on one ofcasing A lids above a rotor coupled at the outside to the package ofrespective rotors by means of shorter spacers 50, located between thering 80 and the respective lid.

The opposite tilting blades 12 located on the front faces of F and Gtype rotors having parallel rotation axes arranged in the same verticalplane can be coupled two by two by means of geared segments 81,permanently engaged, mounted on the ends of the two shafts 15 of theblades, in such a manner as, when driving one of them—further on calledleading blade—the other blade—further on called led blade—should make anidentical movement to the opposite direction, thus achieving thesynchronisation of the movement of the blades located in the samevertical plane.

In the variant of F and G type rotors, having opposite tilting blades12, on the two front faces mounted on in—line shafts, thesynchronisation of the tilting movement of the two blades can beachieved by mounting on the two shafts 15, 78 some cone pinions 82 and83 respectively, permanently engaged with a pinion 94 which, due to thefact it rotates freely on an axle 85 fixed on the rotor, has the role ofreverting the moving direction transmitted from one pinion to the other,all elements being known in themselves.

The blades driving mechanism 12, similar to the one described in theprevious example is installed at all machine stages on the shaft of eachblade belonging to the extreme rotors B, C, E and on the shaft ofleading blade belonging to rotors F, G having the blades on both frontfaces. The cams pairs 24, 25 or 34, 35 and 41, 42 respectively of thedriving mechanism, made according to one of the variants described inthe previous example, are mounted at each stage of the machine onto theassociated drum D so that to assure the simultaneous tilting of theblades located on the same vertical generatrix of the respective packageof rotors.

In another constructional variant, the machine is provided with one pairof cams 24, 25 or 34, 35 and 41, 42 respectively and the adequatedriving mechanisms; according to those previously described, locatedonly at the level of leading blades, either at the first or the laststage of machine, the movement being simultaneously transmitted fromeach of them to all the leading blades on the same vertical, on theother rotors making the package of respective rotors by synchronisationmechanisms consisting of elements known in themselves.

Thus, in the case of package H, J of rotors fixed between them at theoutside by tie-bars 76 and plates 77, all the leading blades areprovided with one pinion 86 fastened on shaft 15 end, outside the rotor,all the pinions 86 on the same vertical being engaged by means of acommon rack 87 located in a casing 88, fixed at the periphery of therotors making the said package, in such a manner as the motiontransmitted from the blade of the first rotor, or, in a constructionalvariant, of the last rotor, is simultaneously transmitted, by rack 87and by gear segments 81 or cone gears 82, 83 and pinion 84 to all theblades on the same generatrix of the rotors package.

In the case of the other package I, K, all the leading blades of thelower and upper levels respectively, of the rotors package are providedwith a driving element, a lever 21, a pinion 26, or a cone pinion 29engaged with a cone gear 30, similarly to the driving elements of theleading blades of the first and last stage respectively, mounted on theshaft 15 end, inside the rotor. For the simultaneous motion transmissionto all the stages of the rotors package, the driving elements of theleading blades at the first stage or the last one respectively, arecoupled to those of the blades located on the same vertical, at theother stages, by means of lining elements: a joint stem 89 hinged tolevers 21 in order to make deforming parallelograms, or a joint verticalrack 90, simultaneously engaged with the pinions 26 from all stages,provided at its upper, or lower end with a shaft 22 and a roller 23 incontact to the surfaces of driving mechanism cam, or a joint shaft 91 onwhich are fixed all the cone gears 30 of the rotors package installed onthe same vertical, the rotors disks making the package being providedwith orifices m′ and c′ permitting the installation of said liningelements.

In the case of rotors F and G having opposite blades on the two faces,in line and loosely mounted on the shaft, the driving mechanism of eachblade consists of cams 41 and 42 attached onto the drums D of eachmachine stage and of twisted springs 44 located in the orifices s′drilled in the hubs f of each blade, as described in the previousexample. The orifices s′ are drilled in the extreme hubs of the twoblades, in such a manner as each blade be driven by spring 44 installedin the associated orifice s′ and tensioned between its gap t′ and afixed point on rotor, that is orifice k′ drilled in the frame 7 for oneof the blades and orifice z′ drilled either in the outer wall of grooveb or in the ring wall 16 for the other blade.

In a constructional variant orifices s′ are drilled in two neighbouringhubs located face to face so that the two blades be simultaneouslydriven by one spring 44 installed in the seating formed of the twoorifices s′ and tensioned between their gaps t′.

EXAMPLE 3

The hydraulic or pneumatic machine with tilting blades, according to theinvention, for working fluids under static pressure.

In view of adjusting the machine to run as a hydraulic or pneumaticmotor using a working fluid under static pressure, in the circular spacebetween the cylindrical shell 1 of stator A and the cylindrical body 45of drum D, interdependent to it, is fixed a cylindrical ring 92 with theheight corresponding to the distance between the front surfaces ofrotors B, C, having on each front face of it a channel a″ of variabledepth, for the action of the tilting blades 12 of the rotor close tosaid surface, the two channels connecting the fluid inlet and outletnozzle, diametrically opposed, each having an initial zone b″, with adepth increasing to the rotation sense of said rotor, on the angularsector γ₁ specific to blade transition from passive to active position,a middle zone c″ open to the other rotor, with constant depth, equal tothe height of the cylindrical ring 92, on the angular sector γ₂,specific to keeping the blade in active position on rotor, and aterminal zone d″, with decreasing depth, on angular sector γ₃, specificto blade transition from active to passive position.

The bottom of channel a″ in the zones with increasing depth b″ anddecreasing depth d″ consists of some shaped surfaces e″ and f″respectively, similar to the surfaces generated by the edge of bladepanel parallel to its rotation axis, at the movement of said tiltingblade through the channel, on the angular sector γ₁ and γ₃ respectively,whereas the lateral walls of the channel consist of an external shapedsurface g″ and an internal shaped one h″, similar to the surfacesgenerated by the other edges of the blade panel, in such a manner as theinterspace between the shaped surfaces of the channel and thecorresponding blade edges should have minimum values during its wholeevolution in the said channel.

The two channels a″ can be served by separate inlet 2—outlet 3 nozzlesor by jointly shared nozzles.

The connection between the inlet nozzle 2 on shell 1 of stator A andeach of the two channels a″ is achieved either separately, by a radialchannel i″ in the cylindrical ring 92, provided with a branch j″communicating to a slot k″ drilled in the shaped surface e″ of theinitial zone b″ of the channel, or by a joint radial channel i″,connected to both branches j″. According to other constructionalvariants, the connection between the radial channel i″ and each channelwith variable depth a″ is achieved either directly by some slots l″ madein one or both lateral faces—the outer one g″ and the inner one h″—onone portion or along the entire initial zone b″ of said channel, or by agroove m″ with variable or constant depth, executed on the bottomsurface e″ on one portion or along the entire initial zone b″,communicating to the radial channel i″ by its branch n″.

The connection between each channel with variable depth a″ and theoutlet nozzle 3 is achieved either by slots o″ drilled on one or bothlateral surfaces—outer g″ and inner h″ one, over the entire length ofthe terminal zone d″ of the channel or by a groove p″ with variable orconstant depth, executed along the bottom surface f″ of terminal zoned′, connected to a slot q″ located on an extension of said channel, thetwo slots q″ being able to merge so that the channels with variabledepth a″ on the two front faces communicate to each other, thecylindrical ring 92 being provided with one or several radial channelsr″ making the connection between the said slots o″, q″ and the outletnozzle 3.

According to a constructional variant, the distance between the frontfaces of the two rotors B, C can be increased, without modifying thetilting blades dimensions 12, by adequately increasing the heights ofthe cylindrical ring 92 and of drum D, the channels a″ having the depthcorrelated to the height of the blade in active position on theassociated rotor and being closed all along their entire length.

In another variant, if the height of cylindrical ring 92 exceeds the sumof the depths of the two channels a″ the length of their shaped zone canbe increased so that for each channel:γ₁+γ₂+γ₃>180°,the plan projections of the two channels overlap over a certain portionwhile the orientation of the driving mechanism cam of the tilting bladesof each rotor B or C corresponds to the plane position of the respectivechannel a″.

In other constructional variants, either the terminal zone d″ of channela″, closed or open, has a constant depth along its whole length, equalto that of the middle zone c″, being eventually devoid of the dischargegroove p″ and communicating directly to slot q″, located on an extensionof said channel, connected to outlet nozzle 3, or the channel a″ isdevoid of the middle zone c″ with constant depth, the initial zone b″being directly connected to the terminal zone d″.

Thus, inside each channel a″ of the cylindrical ring 92, between theadjacent tilting blades 12 of each rotor, are formed some mobilecompartments, demarcated from the active and passive surfaces of saidblades, the rotor front face and the faces of channel a″ over theportion covered between the two blades, the volume of said compartmentsbeing variable due to the blades motion along the channel, on itsvariable depth zones—the initial b″ and eventually the terminal zonesd″—and constant on its middle zone c″.

In view of diminishing the losses due to leaks, the front surfaces ofthe cylindrical ring 92 can be provided with baffles or sealinglabyrinths, known in themselves, not shown on the drawing, arranged onone or both edges of the channel a″, concentrically with the channeland, eventually, at one or both ends of the said channel, to a radialdirection.

In the functional variant as pneumatic motor, the working fluid iseither gas or pressure steam coming from an external storage tank, knownin itself, not shown on the drawing, or gases coming from combustionfuel into a combustion chamber 93 outside the motor, known in itself, orinto a combustion chamber s″ located inside the cylindrical ring 92,both equipped with feeding devices for the formation of fuel mixture andits ignition, all known in themselves, not shown on drawing andconnected by one or several radial channels i″ to the channels withvariable depth a″.

Along the zone with increasing depth b″ of channel a″, the pressure ineach moving compartment between two successive blades, varies with theincrease of its volume, from a maximum feed value, in the compartmentsdirectly connected to the fluid inlet nozzle, or by slot k″ or slots l″or channel m″ executed on part of the said zone, to a minimum value, atthe end of the initial zone b″ and on the middle zone c″ with constantvolume compartments, while subsequently, on the terminal zone d″, due tothe direct connection of each compartment to the outlet nozzle 3 eitherthrough slots o″ or through the grooves p″, slots q″ and channels r″,the pressure decreases to the value of the motor outlet pressure.

Each compartment located on the initial zone b″ of the channel,containing the working fluid under a certain pressure, borders, anytime, upstream on a compartment with lower volume and higher pressureand downstream, on a compartment with higher volume and lower pressureso that the total pressure drop over the entire initial zone b″ occursin a number of pressure stages equal to the number of compartmentslocated at a certain time in the said zone of the channel, the pressuredrops from one compartment to the other through the interstices betweenthe tilting blades and the channel walls they move in, being diminisheddue to the low pressure difference existing between the saidcompartments.

The driving forces causing the rotor movement manifest themselves in allthe compartments located in the initial zone b″ of the channel actingupon the active surfaces of said blades and having values proportionalto the fluid pressure in the compartment and to the depth difference ofthe channel, measured at the top ends of the two blades delimiting thecompartment, the torsion moment of the rotor shaft being the sum of themoments given by all said forces.

In other variants, as hydraulic motor, feeding is done by a pressurefluid, either through the slots l″ or the groove m″ executed along theentire length of the initial zone b″ of the channel a″, the liquidpressure being almost constant in all compartments with growing volume.The liquid discharge from the motor starts at the same time with themotion of the tilting blade on the terminal zone d″ of the channel, thesaid compartment being connected either by slot o″ or by groove p″ onthis zone to the outlet nozzle 3. The driving force acts on the tiltingblades 12 located in the middle zone c″ of channel a″ due to the liquidpressure difference in its two neighbouring zones b″, d″.

In a constructional variant, driving each rotor by a driving momentapplied on its shaft in such a manner as the tilting blades 12 shouldtravel through the channels with variable section a″ to oppositesense—the vertex of the angle between the blade and the front face ofthe rotor oriented to the opposite sense of rotation—the previouslydescribed machine runs as a hydraulic pump or compressor. The workingfluid flows in channel a″ to the sense the rotor blades move, beingsucked in the terminal zone of the channel d″ either by slot o″ or bygroove p″ and slot q″, connected to nozzle 3 which became a suctionnozzle due to the volume increase in the mobile compartments formed onthe rotor when travelling through this zone and discharged by nozzle 2which became a discharge nozzle, at a pressure higher than the suctionone, after being previously compressed eventually—in case of operationwith compressible fluids—due to the volume decrease of the saidcompartment when travelling through the initial zone b″ of the channel.

In other constructional variants, the machine rotors have one or severalconcentric rows of tilting blades 12 which may differ among them, fromone row to the other or from one rotor to the other, in terms of shape,dimensions and position on rotor, each row of blades being provided witha driving mechanism of its own, according to previous examples. On thefront surface of the cylindrical ring 92, close to the front surface ofthe respective rotor, there is a corresponding number of concentricchannels a″₁, a″₂ . . . with variable depth, which can beindependent—with inlet and outlet nozzles of their own—or coupledbetween them, on the same or different faces, either in parallel—withjoint inlet and outlet nozzles for several channels—or in series, one incontinuation to the other, so that the fluid flows the whole way frominlet to outlet, through one or several channels, to the movingdirection of the tilting blades 12, the plane orientation of the camsdriving mechanisms of each row of blade being correlated to that ofchannel a″ wherein the said blades act while the two outlet shafts ofthe machine, coupled to rotors B, C can rotate to the same or toopposite senses.

Each channel a″₁, a″₂ on the face of the cylindrical ring 92 can beframed by baffles or sealing labyrinths, elements known in themselves,not shown on drawing, in order to diminish the pressure losses to theoutside or to the neighbouring channels.

Several constructional variants are possible due to the position of thetilting blades 12 on the rotor faces, as defined by the orientation ofthe angle vertex a formed between the said surface and the blades,against the rotor moving sense, position which can be the same for allrows or may differ from one row to other.

Thus, locating the tilting blades 12 on several concentric rows, id esttwo, in the same position, with the angle vertex α to the rotation senseof the rotor, and the corresponding concentric channels a″₁ and a″₂respectively, one in the continuation to the other, coupled in series byan intermediate shaped channel t″₁₋₂, connecting the slot o″₁ or q″₁ ofthe terminal zone d″₁ of the first channel a″₁ and the slots k″₂ or l″₂or n″₂ of the initial zone b″₂ of the other channel a″₁, the pressuregas gets in by the motor inlet nozzle 2 into the initial zone b″₁ of thefirst channel a″₁ passes successively through the two channels—acting onthe tilting blades of the two rows, found in active position due totheir own driving mechanisms, duly oriented—and goes out of the motor bythe discharge nozzle 3 connected to the terminal zone d″₂ of the otherchannel. By choosing the due dimensions of the channels a″₁ and a″₂ andthe right number of tilting blades 12 on each row, a continuous volumeincrease may be secured for the compartment located between twosuccessive blades and consequently the prolonged expansion of theworking fluid the whole way through, from the circuit inlet to outlet,causing the occurrence of some moving forces which act over the bladeslocated in the initial zone b″₁ and b″₂ of both channels.

According to one constructional variant, by acting each rotor by adriving moment applied on its shaft so that the tilting blades runthrough channels a″₁ and a″₂, coupled in series, to opposite sense,having the angle vertex α in the opposite sense of the rotor movement,the working fluid is sucked by the nozzle 3 of the terminal zone d″₂ ofchannel a″₂ which it is connected to, runs through the two channels,driven by the tilting blades 12, being compressed, due to the continuousvolume decrease of each compartment in the said channels and gets out bythe nozzle 2 connected to the initial zone b″₁ of the other channel a″₁,the machine running as a compressor.

In other constructional variants, the cylindrical ring 92 surface mayhave simultaneously independent channels a″ as well as channelsconnected in parallel or in series, making separate circuits, eachcircuit running according to the orientation of the respective tiltingblades against the rotor, either as an engine or a pump, with the samefluid or different ones. Thus, according to one constructional variant,a pumping circuit achieved with one or several channels a″ supplies airor a fuel mixture under pressure to an outside combustion chamber 93 ora combustion chamber s″ located in the cylindrical ring 92, whence, thegases resulted from combustion circulate through other channels a″,setting into motion the respective tilting blades of the rotor, part ofthe generated energy being used for the feed mixture compression.

In other constructional variants, the hydraulic machine is multistage,according to example two, the rotors with the same diameter or thosewith different diameters having the tilting blades arranged on one orseveral concentric rows, the drum D of each stage having fixed acylindrical ring 92 provided with channels a″, with correspondingvariable section, which can be coupled between them on each stage, aspreviously described, or between stages, in such a manner as to makeinside the machine, either one circuit running as an engine or a pump(compressor), or several circuits of which some are running as an enginewhile the other are running as a pump (compressor), using one or severalworking fluids.

The cylindrical rings 92 located on both sides of the rotor faces arefixed in interdependence to the respective drums D either by means offastening ribs 48 and rings 80 respectively as well as of some fasteningelements—such as bolts, nuts, etc.—or by some space rings 94 locatedbetween the two neighbouring cylindrical rings 92, concentrically tothem—either outside the disk rotors F or inside the ring rotorsG—holding being achieved by bolts and nuts, known in themselves, notshown on the drawing—the space rings 94 can be provided with channels u″and v″ connected to the inlet channels i″ and the outlet channels r″executed into the neighbouring cylindrical rings 92.

The tilting blades on each front face of the intermediate rotors F, Gare driven either by a common mechanism, according to previous examplesor by a mechanism of their own, dismissing eventually the permanentcoupling of the tilting blades located on the opposite faces of a rotor,by geared segments 81, the plane orientation of the cams pairs of theindependent driving mechanism of each stage can be different in thisvariant, from one stage to another, according to the orientation of thechannels with variable section a″ wherein the tilting blades move on therespective stage and row.

In the case of the fluid circuits extended over several stages of themachine, the coupling of the channels a″ located on different stages isdone by some pipes 95, known in themselves, which sake the connectionbetween the radial inlet channels i″ and respectively the radial outletchannels r″ of channels a″ from one stage to those of the next stage,according to the chosen connections plan.

In the case when, in order to make a circuit by coupling the channelsfrom one stage to those of the other stage or to the inlet or outletnozzles of the machine, it is necessary to cross one or severalintermediate stages, their cylindrical rings 92 are provided with radialchannels w″, coupled to the associated connecting pipes 95.

The connecting pipes 95 are located either outside the cylindrical rings92 or inside the drums D, similarly to the fastening elements of theneighbouring drums D as they frame a disk rotor F or ring rotor Grespectively, the position of inlet radial channels i″ and outletchannels r″ respectively—to the outside or the inside of the cylindricalring 92—being chosen so as to suit the position of the respective pipes.The machine inlet—outlet nozzles respectively and the connecting pipes95 coupled to them are located on the circular ring 92 being part of thedrum D which is directly fitted on the machine casing, their numbercorresponding to the number of the existing fluids circuits and to theirway of coupling.

In other constructional variant, the connection between the channels a″of the various stages can be achieved by the channels u″ and y″ existingin the spacing rings 94.

In other constructional variants, in order to reduce the axial forcesresulted in the shafts bearings, the machine has only rotors withtilting blades on both faces, either two disk rotors F, each coupled toone of the outlet shafts, or a package I made up of disk rotors F, eachcoupled directly to one of the machine shafts and a package J made up ofring rotors G and an extreme rotor B or C, devoid of tilting blades onits front face, used only for coupling the whole package to the othermachine shaft by its disk 8 or 9 respectively, extended to the rotorperiphery and its hub 10 or 11 respectively, belonging to it. Thecylindrical rings 92 fitted onto the drums D of each stage have channelsa″ with variable depth on one or both front faces as they occupy insidethe machine an extreme position, bordering one surface of rotor F, G oran intermediate position, between the surfaces provided with tiltingblades of two neighbouring rotors F, G.

In the particular case the tilting blades on the two front faces of eachrotor are identical, as shape and arrangement, and the fluids pressuresin the corresponding channels a″ on the cylindrical rings 92 are equal,the resulting axial force acting on the rotor is null.

In other constructional variants, the hydraulic machine can have onlyone upper outlet shaft 52 or a lower one 53.

Thus, in a constructional variant, the extreme rotors B and C arefastened by their hubs on the same outlet shaft of the machine, theorientation of the tilting blades on the front faces of the rotors andthat of channels a″ on the front faces of the cylindrical ring 92 beingselected so as to make both rotors move to the same sense.

In other constructional variant, the hydraulic machine has one extremerotor B or C, provided with one or several rows of tilting blades 12,the cylindrical ring 92—having, accordingly, one or several channels a″on the surface adjacent to the rotor—being fitted on the lid 5 or 4opposite to the respective rotor.

In another constructional variant, in order to reduce the resultingaxial force acting on the shaft, the hydraulic machine has one rotorwith tilting blades 12 on both faces, similarly to the disk typeintermediate rotor F, previously described, installed on its shaft 52 or53 and two cylindrical rings 92 fitted on the lids 4 and 5 of casing A,on both sides of the rotor, provided on their front faces with thechannels a″, having variable depth, corresponding to the rotor tiltingblades, separated or coupled to one another, in series or in parallel.

In a variant, the hydraulic machine has several disk rotors F withtilting blades 12 on both faces, fastened on a joint shaft 52 or 53,spaced from one another in the form of a package of rotors I and acorresponding number of cylindrical rings 92 with channels a″, havingthe shape and dimensions adequate to the blades of the associated rotor,located either on one front face—in the case of the those located at theends of the rotors package and fitted on upper 4 or lower 5 lids—or onboth front faces—in the case of those located between two neighbouringrotors, eventually fixed on the cylindrical shell 1 of stator A.

In other constructional variants, the machine has one or several rotorswith tilting blades 12 on both faces, similarly to the ring typeintermediate rotor G, previously described, and an extreme rotor B or C,devoid of tilting blades on its front face, all making a package ofrotors J installed on the outlet shaft 52 or 53 by the disk 8 or 9extended to the periphery of the extreme rotor and its hub 10 or 11.

1. A hydraulic or pneumatic machine with vertical shaft, with tiltingblades, characterized by the fact that, in view of converting the energyof a pressure fluid or of a fluid stream into mechanical energy and inview of achieving a simetrical fluid circulation in the machine,consists of a stator (A) made up of a cylindrical shell (I) providedwith two openings radially arranged to diametrically oposeddirections—one for fluid inlet (2), eventually in the form of aconvergent nozzle and one for fluid outlet (3), eventually in the formof a divergent nozzle and two fixed or detachable lids—an upper (4) anda lower (5) one; two coaxial rotors rotating to opposite senses from oneanother—an upper one (B) and a lower one (C)—in form of disks, withparallel front faces, each consisting of a flat ring plane (6) providedon its front face, with several shaped grooves (b), equally spaced,wherein some tilting blades (12) are installed, coupled by means of aframe (7)—for the upper rotor (B)—to a disk (8) provided with a hub(10), fastened by elements known in themselves, onto an upper outletshaft (52)—for the lower rotor (C) respectively—to a disk (9) providedwith a hub (11) fixed on a lower outlet shaft (53), the two shaftsgetting out through some central orifices (w′, x′) of the lids (4, 5)respectively being supported in some radial—axial bearings (54) alsoprovided with sealing elements, known in themselves, the outer ends ofthe shafts being capable to be coupled to a power consumer each of amongthem, through known means, in order to convey the motion to one outletshaft (55); a number of tilting blades (12), each consisting of arectangular panel (c) with a plane face (h) and a lower face, eitherplane (i) and parallel to the upper one, or curve (j), eventuallyprovided with stiffening ribs (k) and a cylindrical hub (f), the outerface of which is tangent to the upper face (h) of the panel, providedwith a central orifice (g) fitted with a shaft (15), each blade (12)being fitted in a groove (b), duly shaped to the lower face of thetilting blade, bordered at the outer end by a plane surface (o) providedwith an orifice (p) and at the other end by a plane surface (q) with anorifice (r), the two orifices being coaxial meant to fasten some radialor axial—radial bearings (13) and (14) respectively, known inthemselves, for hinged connecting of the blade (12) by means of theshaft (15), the grooves (b) being radially arranged on the front face ofeach rotor, so that each blade (12) should have the hub located to themoving sense of the respective rotor; one driving mechanism for eachblade (12) made up of a lever (21) fixed on the end facing the innerside of the blade shaft (15), having at the free and a fixed shaft (22)with a roller (23) freely moving on it, all the rollers (23) on theupper rotor (B) being guided between the guiding front faces—the upperone (w) and the lower one (x) respectively—of a fixed cam (24), whilethose of the tilting blades on the lower rotor (C) between the guidingfront faces—upper (y) and lower (z)—of another circular fixed cam (25),the two cams having the sample profile permitting, during a completerotor rotation, that each tilting blade (12) occupy, due to its owndriving mechanism, during a rotation fraction—defined by a specificangle γ—an active position—on the angular sector γ₂—wherein the upperface (h) of the blade is perpendicular to the rotor front face, or apassive position—on the angular sector γ₄—where the upper face (h) ofthe blade is within the plane of the front surface of the rotor, theblade being situated in the shaped groove (b), or a transition phasefrom passive to active position—on the angular sector γ₁—or from theactive to passive position on the angular sector γ₃—the cams beingsymmetrically arranged against the symmetry plane of the machine so thattheir guiding surfaces assure the symmetrical arrangement of the angularsector γ₁+γ₄ specific to a rotor as compared to those specific to theother rotor against the symmetry plan of the machine; a drum (D)consisting of a central body (45), with a cylindrical outer face, havingthe cams (24, 25) fitted inside, by means of some ribs (40) forinstance, interlocked to a deflector (46) with symmetrical lateralsurfaces (u′) making a sharp angle between them and connected to theoutside face of the body (45), eventually provided with some gaps (v′)having curve surfaces, permitting overlapping of the deflector (46) withthe angular zone γ₁, and a rib (47), diametrically oposed, some fittedwith stiffening plates (48, 49), fixed to the machine stator (A), in thesymmetry plan of the machine, by means of spacers (50) and of oneelements—screws, nuts—known in themselves, so that, inside the machineare formed two symmetrical, semicircular channels (a), havingrectangular passage section, bordered by the front faces of the tworotors (B, C) moving to opposite sense to one another, the inner face ofthe stator (A) and the outer face of the drum (D), each taking over halfof the inlet fluid flow to the machine, the cams (24, 25) profileassuring the tilting of the blades (12) on each of the two rotors inactive position in one of the two semicircular channels (a) so that thefluid pressure in each channel, acting on the lower face (i) or (j) of arotor blade, during the time it is in active position, obstructing thechannel section, determines the movement of respective rotor to theflowing sense of the fluid, whereas, due to the fluid flowing to thesame sense in the two channels (a), the rotors (B, C) rotate to oppositesense.
 2. A hydraulic or pneumatic machine according to claim 1,characterized by the fact that, in a constructional variant, the tiltingblade in active position makes an angle α<90° with the front face ofrespective rotor, for this purpose, its panel having the shape of adistorded rectangular, with two opposite sides (d, e) in the form of anelipse arc, so that, when the blade is in active position, all thepoints on the respective side be on the same cylindrical surface, thegrooves (b) on the rotor face being bordered at their ends by curvesurfaces (s, t) having the same profile as the sides of the blade panel.3. A hydraulic or pneumatic machine according to claims 1, 2,characterized by the fact that, in a constructional variant, the axis ofeach tilting blade makes with the tangent to the inner circular outlineof the plane (6), drawn to the intersection point of respective axis, aβ<90° angle with the vertex facing the rotor moving sense.
 4. Ahydraulic or pneumatic machine, according to claims 1+3, characterizedby the fact that, in a constructional variant, the ring plane (6) withshaped grooves (b) is replaced by an external stiffening ring (16) withorifices (p) for the blade bearings, fixed against frame (7) by means ofrods (17), known in themselves, radially arranged, also used as positionlimiters for the tilting blades (12) in passive position on the rotor,being shaped for this purpose to the blades profile, in order toeventually take over the axial loads due to its own weight, on theexternal ring (16) of the rotor, between the blades bearings (13), someequally spaced bolts (18) being fixed, upon which some guiding rolls(19) with spherical face can freely rotate, those of the upper rotor(B), installed to the ring outside (16), being guided between a planering surface (u) of a cylindrical gap (v) provided at the upper side ofthe shell (1) and the upper lid (4) surface, whereas those of the lowerrotor (C), installed to the ring inside (16), are resting against thelower lid (5) of the stator (A).
 5. A hydraulic or pneumatic machineaccording to claim 4, characterized by the fact that, in aconstructional variant, in the absence of the external ring (16), thetilting blades (12) are bracketed only in bearings (14) installed on theinternal frame (7) of the rotor, also provided with position limiters(20) for blade support in passive position.
 6. A hydraulic or pneumaticmachine according to claims 1+5, characterized by the fact that, in aconstructional variant, the driving element of the blade is a pinion(26) fixed on the end of its shaft (15) and engaged with a tappet withrack (27) provided at the end with the shaft (22) on which, in freerotation, is the roller (23) guided by one of the two cams (24) or (25),the tappet being capable of executing a vertical translation movement ina guide of a casing (28) fixed on the rotor, a guide which can belocated on one side (a′) or the other side (b′) of the pinion, thuscorrelating the rotation sense of the tilting blade (12) to the movementsense of the tappet (27) so that the blade (12) tilting in activeposition occurs during the downward movement of the tappet (27) orduring its upward movement respectively.
 7. A hydraulic or pneumaticmachine according to claims 1+5, characterized by the fact that, in aconstructional variant, the driving element of the blade is a conepinion (29) fixed on the end of its shaft (15) and engaged with a conegear with vertical shaft (30) coaxial and connected to a cylindricalgear (31) provided with a spindle (32) which can freely rotate in abearing (c′) of a protection casing (33) of the mechanism, installed onrotor, the cylindrical gear (31) engaging a rack tappet (27) provided atthe end with the shaft (22) on which the guiding roller (23) freelyrotates, the tappet (27) being capable of executing a horizontaltranslation movement in a guide of the casing (33) that can be locatedon one side (d′) or the other side (e′) of the cylindrical gear (31),thus correlating the moving sense of the tilting blade (12) to themoving sense of the tappet (27) so that the blade (12) tilting in activeposition occurs when the tappet (27) moves to the rotor outside or tothe rotor center, respectively, all guiding rollers (23) of the upperrotor (B) blades being guided between two guiding surfaces—the outer one(f′) and the inner one (g′)—of a fixed radial upper cam (34) whereasthose of the lower rotor (C) are guided between two guiding surfaces—theouter one (h′) and the inner one (i′)—of a fixed radial lower cam (35),the two cams having the same profile, being fixed by means of ribs (40)inside the drum (D) so that they be symmetrically arranged to thesymmetry plane of the machine.
 8. A hydraulic or pneumatic machine,according to claims 1+5, characterized by the fact that, in aconstructional variant, both the upper cam (24) and the lower one (25)have one guiding face each, the permanent contact of the roller (23) tothem being secured by the pressure of the working fluid acted on theactive face of the tilting blade, properly shaped, or by means ofcounterweights (36) properly installed on the lever arm (21) or itsextension (j′), or by some duly stressed spring (37) between a pointlocated on the rotor frame (7), for ex an oriffice (k′), and a pointlocated on the driving lever (21) of blade, for ex. an oriffice (l′),the rotation angle of the lever (21) being limited by means of a stop(38) fitted on the inner face of the frame (7).
 9. A hydraulic orpneumatic machine according to claims 6 and 7, characterized by the factthat, in a constructional variant, the upper cams (24, 34) and the lowercams (25, 35) have one guiding face each, the rollers (23) being kept inpermanent contact with the respective faces, either by the working fluidpressure acting on the active face of the tilting blade, duly shaped, orby means of springs (39) acting properly on the tappets (27).
 10. Ahydraulic or pneumatic machine according to claims 6 and 9,characterized by the fact that, in a constructional variant, the uppercam (24) has only the upper guiding face (w) and is located on the upperlid (4) of the casing (A) whereas the lower cam (25) has only the lowerguiding face (z) and is located on the lower lid (5) of the casing (A),the protection casings (28) of the driving mechanisms of the blades (12)being installed with the guides (a′) or (b′) facing the faces of therespective cams the two rotors (B) and (C) having the disks (8) and (9)respectively provided with some orifices (m′) corresponding to theposition of the guides in order to allow the vertical gliding of tappets(27) with roller (23) under the action of compressed springs (39).
 11. Ahydraulic or pneumatic machine according to claims 1+5, 8, characterizedby the fact that, in a constructional variant, the tilting blades (12)of the upper rotor (B) are guided by an upper front cam (41) whereasthose of the lower rotor (C) by lower front cam (42) fixed on the outerface of the dram (D), at its extremities, the panel of each blade havingfixed on its upper face (b) a skid (43) with one end (r′) of an adequateshape for the contact to the came face, eventually provided with acontact roller, known in itself, located in a gap (p′) of the panel (c),the surface of the skid head being permanently in contact to the guidingfaces (n′) and (o′) of the two cams (41) and (42) respectively due tothe driving mechanism installed on the lever (21) which, under thisvariant is devoid of the guiding roller (23).
 12. A hyde or pneumaticmachine according to claim 11, characterized by the fact that, in aconstructional variant, the tilting blades (12) of the rotors (B) and(C) are each driven by a twisting spring (44) located in an orifice (s′)in lie with the hub (f), located at its end, the ends of the springbeing fixed one in a gap (t′) in the orifice (s′) wall, whereas theother one in the orifice (k′) of the rotor frame (7) so that the spring(44) should be stressed in order to assure the permanent contact betweenthe curved end (r′) of the skid (43) and the guiding face of therespective cam.
 13. A hydraulic or pneumatic machine according to claim11 and 12, characterized by the fact that, in a constructional variant,the tilting blades (12) can freely rotate on their shafts (15) directlyfitted on the rotor in the orifices (p) and (r) provided to this effect,each blade being driven by the twisting spring (44) located in theorifice (s′) of its hub (f).
 14. A hydraulic or pneumatic machineaccording to claims 1+13, characterized by the fact that, in aconstructional variant, in view of diminishing the clearance between theouter edge of the blade in active position on the rotor and thecylindrical face of the casing (A), each semicircular channel (a) isprovided with a cylindrical segment (51) fixed on the inner face of theshell (1) between the front faces of the two rotors (B, C) within thezone covered by the angle γ₂ run by the rotor blade in active position.15. A hydraulic or pneumatic machine according to claims 1+14,characterized by the fact that, in a constructional variant the twocoaxial shafts get out through the same lid of the casing (A), eitherthe upper (4) or the lower (5) one, the rotor adjacent to the respectivelid being fixed onto a tubular shaft (67) having a central channel (y′)getting out through the central orifice (w′), (x′) respectively of therespective lid, resting on it by means of an axial—radial beating (68)also provided with a sealing device, the other rotor being fixed on acentral shaft (66) resting both in an axial—radial bearing (69),provided with a sealing device, mounted in the central channel (y′) ofthe tubular shaft (67) and; eventually, in an additional bearing (70)provided on a lid in its vicinity, the outlet ends of the shafts beingcapable of getting separately coupled by a power consumer or betweenthem, by means known in themselves, in order to convey the motion to oneoutlet shaft (72).
 16. A hydraulic or pneumatic machine according toclaims 1+4, 6+15, characterized by the fact that, in view of increasingthe passage section and, accordingly, the working fluid flow rate in themachine, it has channels (a) for fluid circulation arranged in amultistaged way, having equal or different dimensions from one stage tothe other, in an even number of stage, consisting of a casing (A) insideof which being several rotors grouped by two packages each coupled toone of the motor shafts: a package (H) consisting of two extreme rotorswith a front face each, provided with tilting blades, located face toface, one on a machine shaft—either the upper rotor (B) or the lowerrotor (C), whereas the other, a ring rotor (E), different fromconstructional view point only through the lack of the coupling elementson the machine shaft—the disk (8) or (9) and the hub (10), (11)respectively—and, in case the machine has more than two stages, a numberof intermediate, ring like rotors (G₁, G₂ . . . ) located between theextreme rotors, each consisting of a ring plane (6) fixed on a frame (7)and having two parallel front faces provided with the shaped grooves (b)locating the tilting blades (12), all the rotors of the package (B)having the tilting blades identical or different in terms of size andnumber from one stage to the other and arranged in such a way as toassure them the same moving sense, fixed between them by means offastening plates (77) and same the bars (76), equally spaced on parallelor concurrent directions on their outer outline, so that, the wholepackage (A), by the hub (10) or (11) on the rotor fixed on a shaft (B)or (C), conveys the motion to the respective shaft of the machine (52,67, 53) or (66) depending on the assembling variant chosen; a package(I) consisting of one or several intermediate rotors respectively, inthe form of a disk (F₁, F₂ . . . ) intercalated between the rotors ofthe other package, each consisting of a ring plane (6) fixed on a disk(9) or (8) provided with a hub (11) or (10) coupled to the other shaftof the machine (53, 66, 52) or (67), the plane (6) having two parallelfront faces provided with shaped grooves (b) locating tilting blades(12) similar to those existing on the rotors of the other package (H) atthe respective stage but arranged in such a manner as to assure therotor (F₁, F₂ . . . ) a rotation movement to the opposite sense of therotors of the other package—the distance between the front faces of theneighbouring rotors being constant at all the stages of the machine ordifferent from one stage to the other, depending on blades width—thetiling blades (12) on the two front faces of each intermediate rotor(F₁, F₂ . . . G₁, G₂ . . . ) being either coupled two by two, in view ofsynchronizing their movement, by means os some geared segments (81),permanently engaged, installed on the shaft of each blade, so that whenone is driven—the leading blade—the other—the led blade—shall any momenttake a symmetrical position to it; a number of drums (D₁, D₂ . . . )equal to the number of machine stages, each located between the frontfaces of two neighbouring rotors rotating to opposite sense from oneanother, arranged in the same position with the deflector (46) and rib(47), the extremities of which do not surpass the rotors outline, in thesymmetry plane of the inlet and outlet fluid connection respectively,the neighbouring drums being fixed to one another so that the rotorsmovement be not hindered, either through the outside of the disk likeintermediate rotors (F₁, F₂ . . . ) by means of spacers (79) locatedbetween the fastening plates (48), (49) respectively coupled to thedeflector (46) and to the rib (47) respectively, on each drum, or insidethe frame of the ring like intermediate rotors (G₁, G₂ . . . ) by meansof the spacers (79) located between some fastening rings (80) insideeach drum, as part of its body (45), the whole drums package thus formedbeing fastened onto the casing (A) lid located in the vicinity of theextreme ring rotor (E) by means of shorter spacers (50) placed betweenthe fastening ring (80) on the closest drum (D), to the lid and therespective lid (4) or (5), located inside the rotor frame (E); drivingmechanisms of the tilting blades (12) for all the rotors of the machine,installed on the shaft of each blade or only on the shaft of the leadingblades in the case of intermediate rotors (F₁, F₂ . . . G₁, G₂ . . . )with the blades on the two faces coupled by geared sectors (81), thefixed cams driving the respective mechanisms being arranged in such away as to assure the simultaneous movement of the blades located on thesame vertical generatrix of the respective package of rotors.
 17. Ahydraulic or pneumatic machine according to claim 16, characterized bythe fact that, in a constructional variant, the rotors package fixedbetween them through the inside (I) consists of a single intermediatedisk like rotor (F₁) located in the machine in the vicinity of theextrem rotor (B) or (C) of the other package of rotors (H) and a numberof intermediate ring like rotors (G), all the rotors of the packagebeing rigidly fixed between them by means of the longitudinal tie bars(76) and the fastening plates (77), equally spaced on the inner outlineof each rotor frame (7), inside the drums (D), the whole package ofrotors being coupled to the machine shaft by the hub of the disk likerotor (F₁), the stator (A) having the lid (4) or (5) located in thevicinity of the extreme ring rotor (E) of the rotors package fixed inbetween through the outside (H), shaped to the form of the ring rotors(G) and (E) making the two packages.
 18. A hydraulic or pneumaticmachine according to claim 16, characterized by the fact that, in aconstructional variant, in view of making fluid circulation channels (a)multistaged in an uneven number of stages, has the rotors grouped intotwo packages with an equal number of rotors, each coupled to one of themachine shafts: a package (J) consisting of an extreme rotor, with onefront face, fixed on a machine shaft—either the upper rotor (B) or thelower rotor (C)—and a number of intermediate ring rotors (G₁, G₂, . . .) with two front faces, all the package rotors being fixed between themby means of longitudinal tie bars (76) and of some fastening plates(77), fitted with tilting blades (12) on their front faces arranged insuch a way as to assure them the same rotation sense, the whole packagebeing coupled to the machine shaft (52, 67, 53) or (66) on which theextreme rotor (B) or (C) is fixed by its hub (10) or (11), depending onthe assembling variant chosen; a package (K) consisting of the otherextreme rotor, with one front face—either the lower (C) or the upper (B)rotor—and a number of intermediate disk rotors (F₁, F₂ . . . ) with twofront faces, interspersed between the rotors of the other package (J),all the package rotors fixed each by its hub (11, 10), on the othermachine shaft (53, 66, 52) or (67), having on their front faces thetilting blades (12) arranged in such a way as to assure them the samerotation sense, opposite to the other of rotors (J), between the frontfaces of two neighbouring rotors, rotating to opposite sense from oneanother, existing one drum each (D₁, D₂ . . . ) located, with thedeflector (46) placed in the symmetry plane of the inlet connection, theneighbouring drums being fixed one to the other by means of spacers (79)located between the fastening elements provided on each drum (48, 49,80), the whole package of drums thus formed being fixed on the casing(A) lid located in the vicinity of extreme rotor (C) or (B) as part ofthe package of disk rotors (K), by shorter spacers (50) located at theoutside of the rotor and between the plates (48) and (49) fitted on theclosest drum to the lid and the respective lid (4) or (5).
 19. Ahydraulic or pneumatic machine according to claim 18, characterized bythe fact that, in a constructional variant, the package of rotors fixedbetween them trough the inside (K) consists of a single intermediatedisk rotor (F₁) located in the vicinity of the extreme rotor (B) or (C)of the other package of rotors (J), a number of intermediate ring rotors(G) and an extreme ring rotor (E), all the package rotors being rigidlyfixed between them by means of longitudinal tie-bars (76) and offastening plates (77), equally spaced on the outline of the inner frame(7) of each rotor, inside the drum (D), the whole package of rotorsbeing coupled to the machine shaft by the hub of the intermediate diskrotor (F₁), the stator (A) having the lid (4) or (5) located in thevicinity of the extreme ring rotor (E), shaped to the form of the ringrotors (G) and (E) making the two packages.
 20. A hydraulic or pneumaticmachine according to claims 16+19, characterized by the fact that, thering plane (6) of the intermediate rotors (F, G) with tilting blades onboth front faces is replaced by an external ring (16), concentric withthe inner fame (7), fixed to ft by means of some rods (17) eventuallyarranged radially, which can also serve as position limiters for thetilting blades (12) in passive position, being duly shaped for thisfraction according to the blades profile, both the ring (16) and theframe (7) being provided with coaxial orifices (p) and (r) respectivelyfor the installation of the bearings (13) and (14) respectively of thetilting blades (12) pairs.
 21. A hydraulic or pneumatic machine a toclaims 16+20, characterized by the fact that, in view of reducing thethickness of the intermediate rotors (F, G) the latter have the tiltingblades (12), placed in opposite positions on the two front faces,installed coaxially either in a seat resulting from the crossing of theshaped grooves (b) on the opposite faces of the rotor, or between theouter ring (16) and the inner frame (7), the rotor being provided withone row of coaxial orifices (p, r) for the installation of the jointbearings (13, 14) of the two blades, each blade having on its panel (c)edge one hub consisting of one or several elements (f), alternating withthose making the hub of the pair blade, so as to make together a “hinge”type articulation, the two blades being fitted, by their hubs (f), ontwo coaxial shafts—one filled (15) and one tubular (78, coupled betweenthem by some cone pinions (82) and (83), permanently engaged by a pinion(84) rotating freely on a shaft (85) fixed onto the rotor, thussynchronizing the movement of the two tilting blades (12) when drivingone of them—the leg blade—by means of the driving mechanism installed onits shaft (15, 78).
 22. A hydraulic or pneumatic machine according toclaim 21, characterized by the fact that, the intermediate rotors (F, G)have the tilting blades (12) located in opposite positions on the twofront faces, installed coaxially, each being able of a free movement onthe shaft (15) fixed in the coaxial orifices (p, r) of the rotor, driveneither separately, by a spring (44) fitted in the corresponding orifice(s′) of the hub of each blade and stressed between the gap (t′) made inits wall and a fixed point on the rotor, eventually the orifice (k′) ofthe inner frame (7), an orifice (z′) respectively made either in theouter wall of the groove (b) or in the outer ring wall (16), orsimultaneously by a single spring (44) installed in the seat famed ofthe orifices (s′) drilled in the two neighboring hubs (f) of the twoface to face blades and stressed between the gap (t′) made in theirwalls.
 23. A hydraulic or pneumatic machine according to claims 16+21,characterized by the fact that, in a constructional variant, is providedwith driving mechanism with cams only for the tilting blades (12) on therotors located either at the first or the last stage of the rotorspackage, be movement being simultaneously conveyed from each of them toall the leading blades existing on the same vertical in the respectivepackage of rotors, either, in the case of the rotors package (H, J)fixed between them through the outside, by means of tie-bars (76) andfastening plates (77), by a joint rack (87), located in a casing (88)fitted on the perifery of the rotors making the respective package,engaged with some pinions (86) fixed at the outside of the rotor, on theend of each shaft (15) of the respective leading blades, or, in the caseof the rotors package (I, K) fixed between them through the inside, withtie-bars (76) and fastening plates (77) or directly onto the machineshaft, by some driving elements similar to those of the drivingmechanism—a lever (21) or a pinion (26) or a cone pinion (29) engagedwith a cone gear (30)—installed on the end of each shaft (15) of theleading blades, located inside the rotor frame, the driving elements ofthe blades at all the stages of the rotors package found on the samevertical being coupled by some linking elements: a joint stem (89)hinged to a lever (21) in view of getting distort parallelograms, or ajoint vertical rack (90) which engages simultaneously the pinions (26)from all the stages and is provided at one end with a shaft (22) havingthe roller (23) in touch to the cam face of the driving mechanism, or ajoint shaft (91) on which are fixed all the cone gears (30) of therotors package found on the same vertical, the disks of all rotorsmaking the respective package being provided with orifices (m′)permitting the fitting of the mentioned linking elements (89, 90, 91).24. A pneumatic machine according to claims 1+3, 6+13, 15, characterizedby the fact that, in view of adjusting it to the use of some pressurefluids, within the annular space covered by the cylindrical shell (1) ofthe stator (A) and the cylindrical body (45) of the drum (D),interlocked to it, is provided a cylindrical ring (92) whose heightcorresponds to the distance between the rotors front faces (B, C),having on each front face a groove (a″) with variable depth wherein movethe tilting blades (12) of the rotor bordering the respectivesurface—with baffles or sealing labyrinths, known in themselves,concentrically arranged on one or both edges of the channel, eventuallyat one or both its ends, on a radial direction—the two channels linkingthe inlet and the outlet fluids nozzles, in diametrically opposedpositions, each having an initial zone (b″) with increasing depth to therotation sense of the respective rotor, on the angular sector γ₁characteristic for blade transition from the passive to the activeposition a middle zone (c″) opened towards the other rotor, withconstant depth, equal to the cylindrical ring (92) height, on theangular sector γ₂ characteristic for keeping the blade in activeposition on the rotor, and a terminal zone (d″) with decreasing depth,on the angular sector γ₃ characteristic for the blade transition fromactive to passive position, the bottom and the side walls of the channelhaving the same profile as the surfaces formed by the edges of thetilting blade (12) panel moving in the respective channel, whereas theinterstice between the edges of the blade panel and the channel wallsbeing minimum, so that inside each channel, between the adjacent bladeson each rotor, some compartments are formed with a volume varying duringthe movement of the rotor, to the same sense with the variation of thechannel depth; the pressure working fluid—coming from a storage tank oran outside combustion chamber (93) of a combustion mixture, known inthemselves—entering the machine by a joint feed nozzle (2) or byseparate nozzles (2), each connected to radial inlet channels (l″)executed in the cylindrical ring (92), gets into the initial zone (b″),simultaneously into both channels and separately respectively, into eachone, either by some branches (j″), (u″) respectively of the inletchannel (i″) connected to a slot (k″) made on the shaped face (e″) ofthe channel bottom, and a groove (m″) respectively, with a variable orconstant depth, made along a certain portion of the same surface, or bysome slots (l″) executed along a certain length, in one or both lateralfaces respectively—outside (g″) and inside (h″) one—of the channel,directly connected to the respective inlet channel (i″), the fluidpressure in each compartment covered between two successive blades ofthe rotor decreasing at the same time with the increase of its volumefrom a maximum value, in the compartments directly connected to the feednozzle to a minimum value in the compartments located on the middle zone(c″), so that the driving forces determining the rotor movement shouldbe exerted in all the compartments with increasing volume, located inthe initial zone (b″) of the channel (a″) having variable values withtime, proportional to the fluid instantaneous pressure and with theheight difference between the vertex of the two blades delimitating thecompartment, measured in the respective moment against the front face ofthe rotor, the torsion moment at the shaft of each rotor resulting fromthe sum of the moments given by the respective driving forces; theworking fluid is discharged from each channel (a″) by a common outletnozzle (3) or separate outlet nozzles (3), either by slots (o″) made inone or both the lateral faces—external (g″) or internal (h″)—along theentire length of the terminal zone (d″), communicating by some radialchannels (r″) existing in the cylindrical ring (92) with the respectiveoutlet nozzle (3), or by a groove (p″) with variable or constant depthmade along the bottom surface (f″) of the terminal zone (d″), connectedby slot (q″) to the corresponding radial channels (r″).
 25. A pneumaticmachine according to claim 24, characterized by the fact that, in aconstructional variant, the cylindrical ring (92) is provided with achannel having a closed middle zone (c″), whose depth, correlated to theheight of the tilting blade found in active position on respectiverotor, is lower than the ring height (92), corresponding to the distancebetween the rotors front faces.
 26. A pneumatic machine according toclaims 24, 25, characterized by the fact that, in a constructionalvariant, when the height of the cylindrical ring (92) exceeds the sum ofthe maximum depths of the two channels (a″) on its front faces, thechannels lengths can be increased so as they partially overlap in plane,being eventually connected to their own fluid inlet (2) and outlet (3)nozzles thus becoming independent to one another, the plane arrangementof the driving mechanism cam of the tilting blade (12) of each rotor (B)or (C) corresponding to the plane position of respective channel (a″).27. A pneumatic machine according to claims 24+26, characterized by thefact that, in a constructional variant, the bottom face (f″) profile onthe terminal zone (d″) of the shaped channel (a″) differs from thatdescribed by the blade edges, the channel being able to have on thiszone the same depth as the middle zone (c″), being devoid of thedischarge groove (p″), eventually.
 28. A pneumatic machine according toclaims 25, 26, characterized by the fact that, in a constructionalvariant the channel (a″) of the cylindrical ring (92) is devoid of themiddle zone (c″), the initial zone (b″) with an increasing channel depthbeing directly connected to the terminal zone (d″) with decreasingchannel depth.
 29. A pneumatic machine according to claims 24+27,characterized by the fact that, in a constructional variant, the slots(l″) or the grooves (m″) for the liquid feed to the two channels (a″)are executed over their whole initial zone (b″), the liquid pressurebeing the same in all the compartments with increasing volume, thedriving forces being exerted on the tilting blades (12) located in themiddle zone (c″) of the channel (a″) due to the fluid pressuredifference in the two zones (b″, d″) bordering it.
 30. A hydraulic orpneumatic machine according to claims 24+29, characterized by the factthat, in a constructional variant, by having each rotor driven by amomentum applied on its shaft so that the tilting blades (12) should runthe channels with variable section (a″) to the opposite sense—the angleα vertex between the blade and the front face of the rotor beingarranged to the opposite sense of rotation—operates as a hydraulic pumpor compressor, the working fluid flowing through the variable sectionchannels (a″) to the moving sense of the respective rotor blades, beingsucked in the terminal zone (d″) of the respective channel through thedischarge nozzle (3) becoming the suction nozzle, due to the increase ofthe volum of the mobile compartments formed on the rotor when runningacross this zone, and discharged through the suction nozzle (2) whichbecame the discharge nozzle, at a pressure higher than the suctionpressure.
 31. A hydraulic or pneumatic machine according to claims24+30, characterized by the fact that, in a constructional variant, therotors (B) and (C) have one or several concentric rows of tilting blades(12) that may differ from one another, from one rotor to the other orfrom one row to the other, in terms of shape, dimensions and position onrotor, each row of tilting blades being provided with a drivingmechanism of its own, whereas, on the front face of the cylindrical ring(92), bordering the front face of the respective rotor, is acorresponding number of concentric channels (a₁″, a₂″ . . . ) withvariable depth, framed by baffles or sealing labyrinths eventually, inorder to diminish the pressure losses between the neighbouring channelsor to the outside, the orientation of the driving mechanisms of thetilting blades on each row of the rotor blades being correlated to theplane position of the channel (a₁″, a₂″ . . . ) they run in, eachchannel (a₁″, a₂″ . . . ) having an inlet (2) and outlet (3) connectionof its own, so that on the surface of each rotor are formed independentcircuits with the same or different fluids, the number of which is equalto the number of the concentric rows of tilting blades, the orientationof the angle vertex α formed between the blades of each row and therotor surface—to the rotor moving sense or its oppositesense—determining the operating conditions of each circuit—motor, pumpor compressor respectively, whereas the two outlet shafts of themachine, coupled to the rotors (B, C) can rotate to the same or oppositesenses.
 32. A hydraulic or pneumatic machine according to claim 31,characterized by the fact that, in a constructional variant, thevariable depth channels (a₁″, a₂″ . . . a₁″ . . . a_(n)″) on the same oropposite surfaces of the cylindrical ring (92) are coupled between themeither in series, one in continuation to the other, by a shapedintermediate channel (t_(i, i+1)″) connecting the terminal zone (d″) ofa channel to the initial zone (b_(i+1)″) of the other channel, formingan independent circuit where the working fluid incoming and outgoing iscarried out at the circuits ends whereas, by adequately chosing thesection of each channel and the dimensions and number of the tiltingblades (12) running in it, it is assured the steady increase anddecrease respectively of the volum of each compartment covered betweentwo successive tilting blades along the whole circuit, so that,depending on the moving sense of the blades in the channels, the fluidis subject from the circuit inlet to outlet to a prolongedexpansions—compression respectively, or in parallel with joint inlet andoutlet connections, run to the same sense by the rotor tilting blades,on the cylindrical ring (92) faces eventually existing simultaneouslyindependent circuits formed of one channel and circuits formed ofseveral channels, coupled in series or in parallel, each circuit runningaccording to the tilting blades orientation against the rotor as a motoror as a pump, with the same or different fluids.
 33. A hydraulic orpneumatic machine according to claims 16+32, characterized by the factthat, in a constructional variant, is multistaged, the rotors of eachstage—extreme (B, C) or intermediate (F, G) ones, with the same ordifferent diameters—having the tilting blades arranged on one or severalconcentric rows, each drum (D) being fitted with a cylindrical ring (92)provided with proper channels (a″) with variable depth, the channels(a″) provided at various stages of the machine being capable to becoupled between them by means of pipes (95) connecting the radial inlet(i″)—outlet (r″) channels respectively—from one stage to those of theother stage, according to the conexions plan chosen for the formation ofa circuit, directly, if the two stages are consecutive, or by crossingthe cylindrical rings (92) of the intercalated stages, provided for thispurpose with some properly arranged radial channels (w″), communicatingto the respective connecting pipes (95), the latter being located eitherto the outside of the cylindrical rings (92), or inside the drums (D),in the same way as the fastening elements of the neighbouring drums (D),the position of the inlet (i″)—outlet (r″) radial channels—to theoutside or the inside of the cylindrical ring (92)—being determined bythe position of the respective connecting pipe, whereas the inlet (2)and outlet (3) nozzles of the machine, for each circuit, are located onthe cylindrical ring (92) making part of the drum (D) directly mountedon the machine casing.
 34. A hydraulic or pneumatic machine according toclaim 33, characterized by the fact that, in a constructional variant,the fastening of the cylindrical rings (92) located on both sides of therotors (F, G) faces with tilting blades on the both faces is achieved bymeans of spacing rings (94) placed between the two adjacent, cylindricalrings (92), concentrically to them—either outside the disk rotors (F) orinside the ring rotors (G)—which can be provided with some channels (u″)and (v″), linked to the inlet (i″)—outlet (r″) channels respectively,made in the neighbouring cylindrical rings (92) in order to couple thefluid circuits of the various stages of the machine.
 35. A hydraulic orpneumatic machine according to claims 33, 34, characterized by the factthat, in a constructional variant, the tilting blades (12) on the eachfront face of the intermediate rotors (F, G) are driven by a mechanismof their own, dismissing the permanent coupling of the tilting bladeslocated on the opposite faces of the rotors by geared sectors (81) sothat the cams pairs of the independent driving mechanisms of the bladesat each stage can have a different plane arrangement from one stage tothe other, according to the arrangement of the channels with variablesections (a″) the tilting blades (12) run in, on the respective stageand row.
 36. A hydraulic or pneumatic machine according to claims 33+35,characterized by the fact that, in a constructional variant, in view ofdiminishing the resulting axial forces acting on the two shafts, therotors packages consist only of rotors with tilting blades (12) on bothfaces—either a disk rotor (F) coupled to each of the machine shafts or apackage (I) of disk rotors (F), each coupled directly to one of themachine shaft, and a package (J) consisting of ring rotors (G) and anextreme rotor (B) or (C) devoid of tilting blades on its front face,meant only to couple the whole package (J) to the other machine shaft byits disk (8, 9) respectively, extended up to the machine periphery, andits hub (10, 11) respectively, as part of it, whereas the cylindricalrings (92) fitted on the drums (D) of each stage, have correspondingchannels (a″), with variable depth, on one or both front faces as theyborder one front face with tilting blades (12), in the case of the ringslocated at extremities, or two front faces with tilting blades (12) inthe case of those located in intermediate positions, in the particularcase when the tilting blades on the two front faces of each rotor areidentical as form and arrangement and the fluids pressure in thecorresponding channels (a″) with variable depth are equal, the axialforce is zero.
 37. A hydraulic or pneumatic machine according to claims25+32, characterized by the fact that, in a constructional variant hasboth extreme rotors (B, C) mounted on the same outlet shaft of themachine, the orientation of the tilting blades (12) on the front facesof the rotors and that of the corresponding channels with variable depth(a″) on the cylindrical ring (92) determining the same moving sense ofthe two rotors.
 38. A hydraulic or pneumatic machine according to claims25+32, characterized by the fact that, in a constructional variant, hasa single extreme rotor (B) or (C) provided with one or several rows oftilting blades (12), the cylindrical ring (92) having, accordingly, oneor several channels with variable depth (a″) on the neighbouring face ofthe rotor and being fastened on the lid (5), (4) respectively oppositeto the respective rotor.
 39. A hydraulic or pneumatic machine accordingto claims 25+36, characterized by the fact that, in a constructionalvariant, in view of diminishing the resulting axial force acting on therotor, has either a single disk type rotor (F) with tilting blades (12)on both faces, or several disk type rotors (F) spaced between them, inthe form of package (I) of rotors mounted on a single machine shaft (52)or (53), eventually capable of free axial movement on it, twocylindrical rings (92) with variable depth channels (a″) on one face,mounted on the upper (4) and lower (5) lids of the casing (A) and anumber of cylindrical rings (92) respectively, with variable depthchannels (a″) on both faces, located between the front faces of theneighbouring rotors.
 40. A hydraulic or pneumatic machine according toclaims 25+36, characterized by the fact that, in a constructionalvariant, in view of diminishing the resulting axial forces acting on theshaft, has either a single ring type (G) rotor with tilting blades onboth faces, or several ring type (G) rotors spaced between them, and anextreme rotor (B) or (C) devoid of tilting blades on its front face, allmaking a package of rotors fixed on the motor outlet shaft (52) or (53)by the disk (8) or (9) extended up to the extreme rotor periphery (B) or(C) and by the its hub (10) or (11), or it can freely move axially onthe respective shaft, two cylindrical rings (92) with variable depthchannels (a″) on one face and, eventually, a number of cylindrical rings(92) with variable depth channels (a″) on both faces, located betweenthe neighbouring front faces provided with tilting blades.
 41. Apneumatic machine according to claims 24+28; 30+40, characterized by thefact that, in a constructional variant the working fluid consists of thegases resulting from fuel combustion in a combustion chamber equippedwith devices for the supply, formation and ignition, of fuel mixture,all known in themselves, located either outside (93) or inside (s″) themachine, id est in a cylindrical ring (92) or in a ring spacer (94)connected, by means of the inlet connection (2) by one or several radialchannels (i″) respectively, to the channels with variable depth (a″) ofa motor circuit wherein the tilting blades of the rotors run, thecompression of the air or of the fuel mixture fed into the combustionchamber being achieved either in a separate compressor or in a pumpingcircuit consisting of one or several channels with variable depth (a″)inside the same machine.